WO2008062672A1 - Compresseur - Google Patents
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- Publication number
- WO2008062672A1 WO2008062672A1 PCT/JP2007/071623 JP2007071623W WO2008062672A1 WO 2008062672 A1 WO2008062672 A1 WO 2008062672A1 JP 2007071623 W JP2007071623 W JP 2007071623W WO 2008062672 A1 WO2008062672 A1 WO 2008062672A1
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- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- plane
- central axis
- screw rotor
- groove
- Prior art date
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Classifications
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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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
- F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
- F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
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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
- 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
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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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
- F04C18/54—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
- F04C18/56—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
Definitions
- the present invention relates to a compressor used in, for example, an air conditioner or a refrigerator.
- a cylindrical screw rotor having at least one groove portion that rotates around a central axis and spirally extends around the central axis on an outer peripheral surface, and rotates around the central axis.
- a gate rotor having a plurality of teeth arranged in the circumferential direction on the outer periphery, and the groove of the screw rotor and the teeth of the gate rotor are entangled to form a compression chamber (Japanese Patent Laid-Open No. Hei. 2—See publication 5778).
- this compressor is a so-called CP type single screw compressor.
- CP type means that the screw rotor is formed in a cylinder shape and the gate rotor is formed in a plate shape.
- the gate rotor central axis is parallel to a plane orthogonal to the screw rotor central axis. That is, the tooth portion of the gate rotor is in mesh with the groove portion of the screw rotor along the central axis of the screw rotor.
- a side surface of the gate rotor tooth portion is perpendicular to the gate rotor plane and includes a rotation direction of a tooth center spring of the gate rotor.
- the maximum angle and the minimum angle (hereinafter referred to as the maximum angle and the minimum angle) formed by the side surface of the gate rotor tooth portion and the screw rotor groove wall surface are referred to as the edge angle of the gate rotor, and the edge angle ⁇ in FIG. 1, see ⁇ 2). Disclosure of the invention
- the gate rotor central axis is parallel to a plane orthogonal to the screw rotor central axis, and thus is orthogonal to the gate rotor plane and the gate rotor.
- the angle between the side surface of the screw rotor groove and the side surface of the toothed portion of the gate mouth on the plane including the rotation direction of the central spring of the tooth is the maximum and minimum values. And the difference becomes larger.
- an object of the present invention is to provide a compressor that improves the compression efficiency by reducing the blowhole.
- a compressor according to the present invention provides:
- a cylindrical screw rotor having one groove portion; and a gate rotor having a plurality of tooth portions rotating around a central axis and arranged circumferentially on an outer periphery, the groove portion of the screw rotor and the gate rotor In a compressor that forms a compression chamber by meshing with the teeth of
- the width of change up to is smaller than the change width when the gate rotor central axis is parallel to the plane perpendicular to the screw rotor central axis.
- the edge angle of the seal portion of the gate rotor can be blunted, and the blow hole (leakage gap) existing in the joint portion between the groove portion of the screw rotor and the tooth portion of the gate rotor can be reduced.
- the rate can be improved.
- the wear of the seal part of the gate rotor can be reduced, and the durability Can be improved.
- a cylindrical screw rotor having one groove portion; and a gate rotor having a plurality of tooth portions rotating around a central axis and arranged circumferentially on an outer periphery, the groove portion of the screw rotor and the gate rotor In a compressor that forms a compression chamber by meshing with the teeth of
- a first plane including the screw rotor central axis, a second plane that intersects the screw rotor central axis and intersects the groove of the screw rotor, and is orthogonal to the first plane and the second plane. And a third plane spaced from the groove of the screw rotor,
- the gate rotor central axis passes through the intersection of the first plane, the second plane, and the third plane, and is relative to the second plane when viewed from a direction orthogonal to the third plane. And it is inclined to the same side as the groove part of the screw rotor.
- inclination to the same side means the inclination of the groove portion of the screw rotor with respect to the second plane and the first axis of the gate rotor central axis as viewed from the direction orthogonal to the third plane.
- the inclination with respect to the second plane is the same side as the second plane.
- the gate rotor central axis passes through the intersection of the first plane, the second plane, and the third plane, and is orthogonal to the third plane.
- the side of the groove portion of the screw rotor that comes into contact with the tooth portion of the gate rotor is inclined to the same side as the groove portion of the screw rotor with respect to the second plane as viewed from the direction.
- the change width of the angle of the side surface of the groove portion of the screw rotor with respect to (hereinafter referred to as the screw rotor groove inclination angle) can be reduced.
- the edge angle of the seal portion of the gate rotor that fits the side surface of the groove portion of the screw rotor can be blunted, and the groove portion of the screw rotor and the gate rotor
- the blow hole (leakage gap) that exists in the meshing part with the tooth part can be reduced, and the compression efficiency can be improved.
- wear of the seal portion of the gate rotor can be reduced, and durability can be improved.
- the gate rotor central axis is inclined by 5 ° to 30 ° with respect to the second plane when viewed from a direction orthogonal to the third plane.
- the gate rotor central axis is inclined by 5 ° to 30 ° with respect to the second plane when viewed from the direction orthogonal to the third plane.
- the change width of the screw rotor groove inclination angle can be further reduced.
- the seal portion that contacts the groove portion of the screw rotor in the tooth portion of the gate rotor is formed in a curved surface shape.
- the seal portion that contacts the groove portion of the screw rotor in the tooth portion of the gate rotor is formed in a curved surface shape, It is possible to reduce the leakage of the compressed fluid from the mating portion with the groove portion of the screw rotor, thereby improving the compression performance. Further, it is possible to improve the wear resistance of the meshing portion between the tooth portion of the gate rotor and the groove portion of the screw rotor.
- the compressor of the present invention the axial direction from one end of the screw rotor to the other end at the inclination angle of the side surface of the groove portion of the screw port that contacts the tooth portion of the gate rotor with respect to the circumferential direction of the gate rotor.
- the width of change up to is smaller than the change width when the gate rotor central axis is parallel to the plane perpendicular to the screw rotor central axis, so the blowhole can be reduced and the compression efficiency is improved. it can.
- the gate rotor central axis passes through the intersection of the first plane, the second plane, and the third plane, and is on the third plane. Since it is inclined to the same side as the groove portion of the screw rotor with respect to the second plane as viewed from the orthogonal direction, it is possible to reduce the blow hole and improve the compression efficiency.
- FIG. 1 is a simplified configuration diagram showing an embodiment of a compressor of the present invention.
- FIG. 2 is a simplified front view of the compressor. 3] A simplified side view of the compressor.
- FIG.5 Gate rotor sag when the number of groove portions of the screw rotor is 3 and the number of teeth of the gate rotor is 12, and the gate rotor central axis inclination angle ⁇ is 0 ° 6 is a graph showing a relationship between an alignment angle ⁇ and a screw rotor groove inclination angle 0;
- FIG. 6 When the number of groove portions of the screw rotor is 3, the number of teeth of the gate rotor is 12, and the gate rotor central axis inclination angle ⁇ is 2.5 °, the gate rotor 6 is a graph showing the relationship between the squeezing angle ⁇ and the screw rotor groove inclination angle 0;
- FIG. 7 Gate rotor sag when the number of groove portions of the screw rotor is 3 and the number of teeth of the gate rotor is 12, and the gate rotor central axis inclination angle ⁇ is 5 ° 6 is a graph showing a relationship between an alignment angle ⁇ and a screw rotor groove inclination angle 0;
- FIG. 8 When the number of groove portions of the screw rotor is 3, the number of teeth of the gate rotor is 12, and the gate rotor central axis inclination angle ⁇ is 7.5 °, the gate rotor 6 is a graph showing the relationship between the squeezing angle ⁇ and the screw rotor groove inclination angle 0;
- Gate rotor sag when the number of groove portions on the screw rotor is 6 and the number of teeth on the gate rotor is 12, and the gate rotor central axis inclination angle ⁇ is 0 ° 6 is a graph showing a relationship between an alignment angle ⁇ and a screw rotor groove inclination angle 0;
- FIG.10 Gate rotor meshing when the number of groove portions on the screw rotor is 6 and the number of teeth on the gate rotor is 12, and the gate rotor central axis inclination angle ⁇ is 5 ° 6 is a graph showing the relationship between the angle ⁇ and the screw rotor groove inclination angle 0;
- FIG.11 Gate rotor meshing when the number of grooves on the screw rotor is 6 and the number of teeth on the gate rotor is 12, and the gate rotor central axis tilt angle ⁇ force is 10 ° 6 is a graph showing the relationship between the angle ⁇ and the screw rotor groove inclination angle 0;
- FIG.12 Gate rotor meshing when the number of groove portions on the screw rotor is 6 and the number of teeth on the gate rotor is 12, and the gate rotor central axis tilt angle ⁇ force is 15 ° 6 is a graph showing the relationship between the angle ⁇ and the screw rotor groove inclination angle 0;
- FIG.14 The number of grooves on the screw rotor is 3, and the number of teeth on the gate rotor is 10. It is a graph showing the relationship between the gate rotor central axis tilt angle ⁇ and the leakage influence level at a certain time.
- FIG. 15 is a graph showing the relationship between the gate rotor central axis tilt angle ⁇ and the leakage influence degree when the number of groove portions of the screw rotor is 6 and the number of teeth portions of the gate rotor is 10. Best mode for carrying out
- Fig. 1 shows a simplified configuration diagram as an embodiment of the compressor of the present invention.
- the compressor includes a cylindrical screw rotor 1 that rotates around a central axis la and has at least one groove portion 10 that spirally extends around the central axis la on the outer peripheral surface, and a center.
- a disk-shaped gate rotor 2 having a plurality of teeth 20 rotating around the shaft 2a and arranged circumferentially on the outer periphery, and the groove 10 of the screw rotor 1 and the teeth 20 of the gate rotor 2 Are mixed together to form the compression chamber 30.
- this compressor is a so-called CP type single screw compressor.
- CP type means that the screw rotor 1 is formed in a cylinder shape and the gate rotor 2 is formed in a plate shape.
- This compressor is used, for example, in an air conditioner or a refrigerator.
- Two gate rotors 2 are arranged on both sides of the screw rotor 1 around the screw rotor central axis la.
- the gate rotor 2 follows the center of the gate rotor due to the meshing of the groove portion 10 and the tooth portion 20. Rotate around axis 2a in the direction of the arrow.
- At least one screw thread 12 extending in a spiral shape around the screw rotor central axis la is provided, and between the adjacent screw threads 12, 12, A groove 10 is formed.
- One groove portion 10 is engaged with one tooth portion 20, and the side surface 11 (that is, the seal portion) of the tooth portion 20 contacts the side surface 11 of the groove portion 10 to seal the compression chamber 30.
- the tooth portion 20 is rotated by the side surface 11 of the groove portion 10.
- a casing (not shown) having a slit capable of rotating the gate rotor 2 is attached to the outer peripheral surface of the screw rotor 1. The space force closed by the groove portion 10, the tooth portion 20, and the casing becomes the compression chamber 30.
- the casing is provided with a suction port (not shown) communicating with the groove portion 10 on one axial end surface side of the screw rotor 1.
- the casing is provided with a discharge port (not shown) that communicates with the groove 10 on the other axial end surface side of the screw rotor 1.
- a fluid such as a refrigerant gas introduced from the suction port into the groove 10 is rotated by the screw rotor 1 and the gate rotor 2 to compress the compression chamber 30.
- the compression chamber 30 compresses the volume.
- the compressed fluid is discharged from the discharge port.
- the first plane S 1 including the screw rotor central axis la and the groove 10 of the screw rotor 1 intersect with the first plane S 1 perpendicular to the screw rotor central axis la.
- a second plane S2 and a third plane S3 perpendicular to the first plane S1 and the second plane S2 and spaced from the groove 10 of the screw rotor 1
- the gate rotor central axis 2a is on the third plane S3 and passes through the intersection point P of the first plane Sl, the second plane S2, and the third plane S3.
- the gate rotor central axis 2a is inclined to the same side as the groove 10 of the screw rotor 1 with respect to the second plane S2 when viewed from a direction orthogonal to the third plane S3.
- the inclination angle ⁇ of the gate rotor central axis 2a with respect to the second plane S2 is preferably 5 ° to 30 °.
- inclination to the same side means the inclination of the groove portion 10 of the screw rotor 1 with respect to the second plane S2 and the center of the gate rotor as viewed from the direction orthogonal to the third plane S3. It means that the inclination of the axis 2a with respect to the second plane S2 is on the same side with respect to the second plane S2.
- the distance L between the gate rotor central axis 2a and the screw rotor central axis la (hereinafter referred to as the inter-axis distance L) is, for example, the gate rotor 2 of Outside diameter D from 0 ⁇ 7 to ⁇ ⁇ 2 times (0.7D ⁇ L ⁇ 1.2D).
- the angle formed by the line with respect to the reference line parallel to the screw rotor central axis la is referred to as the gate rotor engagement angle ⁇ .
- the gate rotor engagement angle ⁇ is the sag of the gate rotor 2 described above. It is measured from the beginning.
- FIG. 4 shows the minimum meshing diameter, the intermediate diameter, and the maximum diameter of the gate rotor 2 at the portion of the tooth portion 20 of the gate rotor 2 that meshes with the groove 10 of the screw rotor 1.
- the side surface on the downstream side in the rotational direction of the gate rotor 2 is a reading side surface 20a
- the side surface on the upstream side in the rotational direction of the gate rotor 2 is an unreading side surface 20b.
- FIGS. 5 to 8 when the inclination angle ⁇ (see FIG. 2) of the gate rotor central axis 2a is changed to 0 °, 2.5 °, 5 °, 7.5 °, The relationship between the gate rotor meshing angle ⁇ (see Fig. 4) and the screw rotor groove inclination angle / 3 is shown.
- the maximum and intermediate diameters (see FIG. 4) of the gate rotor 2 on the leading side surface 20a and the unleading side surface 20b (see FIG. 4) are shown.
- the number of grooves 10 in the screw rotor 1 is 3, and the number of teeth 20 in the gate rotor 2 is 12.
- the screw rotor groove inclination angle ⁇ is a value (indicated by an arrow RG) of the gate rotor 2 at a portion in contact with the side surface 11 of the groove 10 of the screw rotor 1.
- the screw rotor groove inclination angle 0 is indicated by a positive value (+ direction) on the gate rotor rotation direction (arrow RG direction) side with respect to the plane St, and the gate rotor rotation direction (arrow RG direction)
- the opposite side is indicated by a negative value (-direction).
- FIG. 5 shows a case where the inclination angle ⁇ of the gate rotor central axis 2a is 0 °, and the gate rotor 2 is in contact with each other on the reading side surface 20a and the unreading side surface 20b.
- the change width of the screw rotor groove inclination angle / 3 is shown.
- FIG. 6 shows the case where the inclination angle ⁇ of the gate rotor central axis 2a is 2.5 °, and the screw rotor groove inclination angle is larger than the change width of the screw rotor groove inclination angle / 3 shown in FIG. The change width of / 3 is getting smaller.
- FIG. 7 shows a case where the inclination angle of the gate rotor central axis 2a is 5 °.
- the screw one rotor groove inclination angle of the leading side surface 20a is increased. While / 3 becomes smaller, the screw rotor groove inclination angle ⁇ of the unleading side surface 20b becomes larger, so that the blow hole can be made smaller.
- FIG. 8 shows a case where the inclination angle of the gate rotor central axis 2a is 7.5 °, and the screw rotor groove on the leading side surface 20a increases as the gate rotor engagement angle ⁇ increases. While the inclination angle is significantly smaller than that in FIG. 7, the screw rotor groove inclination angle / 3 on the unreading side surface 20b is significantly larger than that in FIG. 7, so that the blow hole can be further reduced.
- FIGS. 9 to 12 show that the inclination angle ⁇ (see FIG. 2) of the gate rotor central axis 2a is 0 °
- the relationship between the gate rotor meshing angle ⁇ (see Fig. 4) and the screw rotor groove inclination angle 0 when changing to 5 °, 10 ° and 15 ° is shown.
- the maximum and intermediate diameters (see FIG. 4) of the gate rotor 2 on the leading side surface 20a and the unleading side surface 20b (see FIG. 4) are shown.
- the number of the groove portions 10 of the screw mouth 1 is 6, and the number of the tooth portions 20 of the gate rotor 2 is 12.
- FIG. 9 shows a case where the inclination angle ⁇ of the gate rotor central axis 2a is 0 °, and the gate rotor 2 is in contact with each other on the reading side surface 20a and the unreading side surface 20b.
- the change width of the screw rotor groove inclination angle / 3 is large.
- FIG. 10 shows the case where the inclination angle ⁇ of the gate rotor central axis 2a is 5 °, and the screw rotor groove inclination angle / 3 rather than the change width of the screw rotor groove inclination angle / 3 shown in FIG. The range of change is getting smaller.
- FIG. 11 shows a case where the tilt angle of the gate rotor central axis 2a is 10 °. As the one rotor contact angle ⁇ increases, the screw rotor groove inclination angle on the leading side surface 20a decreases, while the screw rotor groove inclination angle / 3 on the unleading side surface 20b increases.
- the blow hole can be made smaller.
- FIG. 12 shows a case where the inclination angle of the gate rotor central axis 2a is 15 °, and the inclination angle of the screw rotor groove on the leading side surface 20a as the gate rotor engagement angle ⁇ increases. Is significantly smaller than that of FIG. 11, while the screw rotor groove inclination angle / 3 of the unreading side surface 20b is significantly larger than that of FIG. 11, so that the blow hole can be further reduced. Yes.
- the seal portions 21a, 21b in contact with the groove portion 10 of the screw rotor 1 in the tooth portion 20 of the gate rotor 2 are formed in a curved surface shape.
- leading side seal portion 21a is formed on the leading side surface 20a of the tooth portion 20
- the unleading side seal portion 21b is formed on the unleading side surface 20b of the tooth portion 20.
- Blow holes (leakage gaps) 40, 50 indicated by knots and pinchings exist in the meshing portion between the groove 10 of the screw rotor 1 and the tooth portion 20 of the gate rotor 2.
- the leading side blow hole 40 (shown by hatching) exists upstream of the screw rotor 1 in the moving direction (from the compression chamber 30 side shown by hatching) relative to the leading side seal portion 21a.
- an unleading side blow hole 50 (shown by hatching) is present on the upstream side in the moving direction of the screw rotor 1 (on the compression chamber 30 side) from the unleading side seal portion 21b.
- Fluid force compressed in the compression chamber 30 Leaks out of the casing 3 (shown in phantom lines) through the blow holes 40 and 50.
- FIG. 14 and FIG. 15 show the relationship between the inclination angle ⁇ (see FIG. 2) of the gate rotor central axis 2a and the leakage influence degree.
- Leakage influence of leading side blowhole 40 see Fig. 13
- leakage influence degree of unleading side blowhole 50 see Fig. 13
- the total leakage effect degree of the leading side blow hole 40 and the unleading side blow hole 50 is shown below.
- the leakage influence degree is obtained by correcting the respective areas of the leading-side blowhole 40 and the unleading-side blowhole 50 to the leakage amount
- the inclination angle ⁇ of the gate rotor central axis 2a is the same as the conventional one. Shows the degree! / When the angle is 0 °.
- FIG. 14 shows the degree of leakage influence when the number of the groove portions 10 of the screw rotor 1 is three and the number of the tooth portions 20 of the gate rotor 2 is twelve.
- the inclination angle ⁇ of the gate rotor central axis 2a is around 7 °, the influence of leakage is minimized, and the compression efficiency is improved.
- FIG. 15 shows the degree of leakage influence when the number of the groove portions 10 of the screw rotor 1 is six and the number of the tooth portions 20 of the gate rotor 2 is twelve.
- the leakage influence is minimized, and the compression efficiency is improved.
- the gate rotor central axis 2a passes through the intersection point P of the first plane S1, the second plane S2, and the third plane S3, and the first plane S1.
- the third plane S3 In view of the directional force perpendicular to the third plane S3, it is inclined to the same side as the groove 10 of the screw rotor 1 with respect to the second plane S2, so that it contacts the tooth portion 20 of the gate rotor 2.
- the side surface of the groove portion 10 of the screw rotor 1 contacts the side surface 11 of the groove portion 10 of the screw rotor 1. (That is, approximately 90 ° with respect to the circumferential direction of the gate rotor), and the change width of the screw inlet groove inclination angle 0 can be reduced.
- the circumferential direction of the gate rotor 2 is, in other words, the rotational direction of the tooth portion 20 of the gate rotor 2 that contacts the side surface 11 of the groove portion 10 of the screw rotor 1.
- the width of change from the radially outer side to the inner side of the screw rotor 1 means that all the groove portions 10 from the radially outer side to the inner side of the screw rotor 1 that are simultaneously in contact with the teeth 20 of the gate rotor 2. Change the angle of inclination! Accordingly, the edge angle ⁇ 1, ⁇ 2 (see FIG. 13) of the seal portion of the gate rotor 2 that meshes with the side surface of the groove portion 10 of the screw rotor 1 can be blunted, and the groove portion 10 of the screw rotor 1 can be reduced.
- the blow hole (leakage gap) existing in the meshing portion with the tooth portion 20 of the gate rotor 2 can be reduced, and the compression efficiency can be improved.
- wear of the seal portion of the gate rotor 2 can be reduced, and durability can be improved.
- the angle of the side surface of the groove portion 10 of the screw rotor 1 that contacts the tooth portion 20 of the gate rotor 2 is determined by the gate port central axis 2a. It has been found that it changes by inclining with respect to a plane orthogonal to the screw rotor central axis la.
- the inclination angle ⁇ of the gate rotor central axis 2a is preferably 5 ° to 30 °, and the change width of the screw rotor groove inclination angle 0 can be further reduced.
- seal portions 21a and 21b in contact with the groove portion 10 of the screw rotor 1 in the tooth portion 20 of the gate rotor 2 are formed in a curved surface shape, It is possible to reduce the leakage of the compressed fluid from the meshing part with the groove 10 of the screw rotor 1 and improve the compression performance. Further, it is possible to improve the wear resistance of the meshing portion between the tooth portion 20 of the gate rotor 2 and the groove portion 10 of the screw rotor 1.
- the seal portions 21 a and 21 b of the gate rotor 2 can be formed in a curved surface.
- the groove portion 10 of the screw rotor 1 is processed by an end mill, and the seal portions 21 a and 21 b of the tooth portion 20 of the gate rotor 2 are formed into a curved shape by an end mill, so that the maximum inclination angle is obtained.
- the present invention is not limited to the above-described embodiment.
- the quantity of the gate rotor 2 can be increased or decreased freely.
- the seal portions 21 a and 21 b in contact with the groove portion 10 of the screw rotor 1 in the tooth portion 20 of the gate rotor 2 may be formed in an acute angle shape.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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CN2007800411613A CN101535650B (zh) | 2006-11-24 | 2007-11-07 | 压缩机 |
EP07831354.1A EP2090784A4 (en) | 2006-11-24 | 2007-11-07 | COMPRESSOR |
US12/515,517 US8105059B2 (en) | 2006-11-24 | 2007-11-07 | Compressor with screw rotor and gate rotor with inclined gate rotor center axis |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006-316793 | 2006-11-24 | ||
JP2006316793A JP4169069B2 (ja) | 2006-11-24 | 2006-11-24 | 圧縮機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008062672A1 true WO2008062672A1 (fr) | 2008-05-29 |
Family
ID=39429610
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2007/071623 WO2008062672A1 (fr) | 2006-11-24 | 2007-11-07 | Compresseur |
Country Status (5)
Country | Link |
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US (1) | US8105059B2 (ja) |
EP (1) | EP2090784A4 (ja) |
JP (1) | JP4169069B2 (ja) |
CN (1) | CN101535650B (ja) |
WO (1) | WO2008062672A1 (ja) |
Cited By (2)
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US8022032B2 (en) | 2004-11-19 | 2011-09-20 | Smithkline Beecham Corporation | Method for customized dispensing of variable dose drug combination products for individualizing of therapies |
WO2023188988A1 (ja) * | 2022-03-28 | 2023-10-05 | ダイキン工業株式会社 | スクリュー圧縮機及び冷凍装置 |
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Publication number | Priority date | Publication date | Assignee | Title |
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JP2011038484A (ja) * | 2009-08-13 | 2011-02-24 | Mitsui Seiki Kogyo Co Ltd | スクリューコンプレッサのゲートロータの稜線廻りの構造 |
US9057373B2 (en) | 2011-11-22 | 2015-06-16 | Vilter Manufacturing Llc | Single screw compressor with high output |
CN103122857B (zh) * | 2012-09-29 | 2015-11-18 | 苏州利森空调制冷有限公司 | 一种压缩机用的带螺钉状转子的压缩组件 |
JP7364949B2 (ja) * | 2022-03-28 | 2023-10-19 | ダイキン工業株式会社 | シングルスクリュー圧縮機 |
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JPS49121207A (ja) * | 1973-03-20 | 1974-11-20 | ||
JPH025778A (ja) | 1987-12-03 | 1990-01-10 | Bernard Zimmer | 高圧下の流動体を処理する方法及びスクリュウ装置 |
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FR1601531A (ja) * | 1968-12-27 | 1970-08-24 | ||
GB1388537A (en) * | 1973-03-13 | 1975-03-26 | Zimmern B | Rotary positive-displacement machines for compression or expansion of a fluid |
DE2315503C2 (de) * | 1973-03-28 | 1983-03-31 | Omphale S.A., Puteaux, Hauts-de-Seine | Außenachsige Rotationskolben-Verdichtungs-oder Expansionsmaschine |
US4179250A (en) * | 1977-11-04 | 1979-12-18 | Chicago Pneumatic Tool Company | Thread construction for rotary worm compression-expansion machines |
FR2444180A1 (fr) * | 1978-12-13 | 1980-07-11 | Zimmern Bernard | Machines volumetriques a vis et pignon comprenant plusieurs aretes de contact |
AU1016801A (en) * | 1999-10-26 | 2001-05-08 | Shiliang Zha | A single screw compressor |
CN1079501C (zh) * | 1999-10-26 | 2002-02-20 | 查世樑 | 单螺杆压缩机 |
CN1532404A (zh) * | 2003-03-24 | 2004-09-29 | 朱妙睿 | 同轴多节蜗杆式空气压缩机 |
-
2006
- 2006-11-24 JP JP2006316793A patent/JP4169069B2/ja not_active Expired - Fee Related
-
2007
- 2007-11-07 WO PCT/JP2007/071623 patent/WO2008062672A1/ja active Application Filing
- 2007-11-07 CN CN2007800411613A patent/CN101535650B/zh not_active Expired - Fee Related
- 2007-11-07 EP EP07831354.1A patent/EP2090784A4/en not_active Withdrawn
- 2007-11-07 US US12/515,517 patent/US8105059B2/en not_active Expired - Fee Related
Patent Citations (3)
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US1989552A (en) * | 1934-01-03 | 1935-01-29 | Paul E Good | Rotary compressor |
JPS49121207A (ja) * | 1973-03-20 | 1974-11-20 | ||
JPH025778A (ja) | 1987-12-03 | 1990-01-10 | Bernard Zimmer | 高圧下の流動体を処理する方法及びスクリュウ装置 |
Non-Patent Citations (1)
Title |
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See also references of EP2090784A4 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8022032B2 (en) | 2004-11-19 | 2011-09-20 | Smithkline Beecham Corporation | Method for customized dispensing of variable dose drug combination products for individualizing of therapies |
WO2023188988A1 (ja) * | 2022-03-28 | 2023-10-05 | ダイキン工業株式会社 | スクリュー圧縮機及び冷凍装置 |
JP7360065B1 (ja) | 2022-03-28 | 2023-10-12 | ダイキン工業株式会社 | スクリュー圧縮機及び冷凍装置 |
JP2023154430A (ja) * | 2022-03-28 | 2023-10-20 | ダイキン工業株式会社 | スクリュー圧縮機及び冷凍装置 |
Also Published As
Publication number | Publication date |
---|---|
JP4169069B2 (ja) | 2008-10-22 |
EP2090784A4 (en) | 2014-01-22 |
EP2090784A1 (en) | 2009-08-19 |
CN101535650B (zh) | 2011-08-03 |
US8105059B2 (en) | 2012-01-31 |
JP2008128167A (ja) | 2008-06-05 |
US20100074785A1 (en) | 2010-03-25 |
CN101535650A (zh) | 2009-09-16 |
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