EP2998585B1 - Compresseur à volute - Google Patents

Compresseur à volute Download PDF

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Publication number
EP2998585B1
EP2998585B1 EP14830230.0A EP14830230A EP2998585B1 EP 2998585 B1 EP2998585 B1 EP 2998585B1 EP 14830230 A EP14830230 A EP 14830230A EP 2998585 B1 EP2998585 B1 EP 2998585B1
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EP
European Patent Office
Prior art keywords
wrap
inner circumferential
outer circumferential
tip seal
rotation angle
Prior art date
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Active
Application number
EP14830230.0A
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German (de)
English (en)
Other versions
EP2998585A4 (fr
EP2998585A1 (fr
Inventor
Hajime Sato
Hisao Mizuno
Takahide Ito
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.)
Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP2998585A1 publication Critical patent/EP2998585A1/fr
Publication of EP2998585A4 publication Critical patent/EP2998585A4/fr
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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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0276—Different wall heights
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid

Definitions

  • the present invention relates to a scroll compressor.
  • a scroll compressor is equipped with a fixed scroll and an orbiting scroll.
  • Each of the fixed scroll and the orbiting scroll is a disk-shaped end plate provided with a spiral wrap on one surface side.
  • Such a fixed scroll and an orbiting scroll are arranged to face each other with their wraps intermeshed, and the orbiting scroll is caused to revolve with respect to the fixed scroll.
  • a compression chamber between both of the scrolls is filled with a gas drawn through the outermost circumferential portions of the wraps.
  • the gas is compressed as the volume of the compression chamber decreases with the revolution of the orbiting scroll.
  • the gas is discharged through a port positioned at the central portion of the end plate in a maximally compressed state.
  • the fixed scroll and the orbiting scroll are each provided with a tip seal at its tip of the wrap.
  • the compressed gas is introduced into seal grooves accommodating the tip seals.
  • Each tip seal is pressed against the end plate by a back pressure caused by the compressed gas to seal a clearance between the wraps and the end plates.
  • a tip seal is divided into two parts in a circumferential direction, and the divided two seals are connected together.
  • the tip seal positioned at an inner circumferential side of each wrap is formed from a material more excellent in heat-resistance and abrasion-resistance than that of the tip seal positioned at an outer circumferential side.
  • each tip seal is placed as divided into portions at the inner and outer circumferential sides of the step of the wrap as described in Patent Literature 2.
  • each tip seal is inevitably divided into portions at inner and outer circumferential sides of the step of the wrap as in Patent Literature 2.
  • each tip seal is divided into portions on both sides of the step of the wrap, and aims to improve the reliability of the 3D-type scroll compressor by improving the durability of the tip seals.
  • the present invention is a scroll compressor including a fixed scroll and an orbiting scroll, the fixed scroll and the orbiting scroll each having a spiral wrap configured to decrease in height from an outer circumferential side to an inner circumferential side via a stepped portion and an end plate having a stepped wall being erected following the stepped portion of the counterpart wrap.
  • an inner circumferential tip seal provided in an inner circumferential side of the stepped portion and lying between the wrap and the counterpart end plate and an outer circumferential tip seal provided in an outer circumferential side of the stepped portion and lying between the wrap and the counterpart end plate are different in material at least at portions facing the end plate and the step portion is positioned in an outer circumferential side of a rotation angle corresponding to a central value of a temperature range within which a temperature of the wrap rises, and within a rotation angle range exceeding 2 ⁇ in an inner circumferential side from a rotation angle at an outermost circumferential portion of the wrap.
  • the inner circumferential tip seal can be formed from a material satisfying a desired condition based on the temperature and the pressure of the central portion of each scroll, and the outer circumferential tip seal can be formed from other, inexpensive material.
  • the durability of the tip seals can be improved while holding down the cost, compared with the case in which both the inner and outer circumferential tip seals are formed from the same material.
  • An object of the present invention can be achieved if the inner circumferential tip seal and the outer circumferential tip seal are formed from different materials at least at the portions facing the end plate.
  • the stepped portion be positioned in an outer circumferential side of a rotation angle corresponding to a central value of a temperature range within which a temperature of the wrap rises from a rotation angle at an outermost circumferential portion of the wrap to a rotation angle at an innermost circumferential portion of the wrap, and that the inner circumferential tip seal be formed from a material satisfying at least one requirement of a higher heat resistant temperature, a smaller comparative abrasion quantity, and a smaller linear expansion coefficient than those of a material of the outer circumferential tip seal.
  • heat resistant temperature means an upper-limit temperature causing no change in appearance or no decrease in mechanical properties to a tip seal when it is used continuously.
  • abrasion quantity is obtained by dividing the abrasion quantity expressed in volume by the distance a tip seal has slid and the vertical load.
  • a material that is hardly abraded has a small comparative abrasion quantity.
  • a tip seal formed of a material having a small linear expansion coefficient can avoid being strongly pressed against the end plate due to the heat expansion, and is therefore hardly abraded.
  • the comparative abrasion quantity and the linear expansion coefficient are measures associated with the abrasion resistance showing how small a volume is that is reduced under friction.
  • durability of a tip seal as used herein includes heat resistance expressed by the heat resistant temperature, and the above abrasion resistance.
  • the present invention also encompasses a configuration in which the materials of each of the inner circumferential tip seal and the outer circumferential tip seal are different only at the portions facing the end plate.
  • Examples of such a configuration include one in which a heat resistant temperature of a material of the portion of the inner circumferential tip seal facing the end plate is higher than that of a material of the portion of the outer circumferential tip seal facing the end plate, one in which a comparative abrasion quantity of a material of the portion of the inner circumferential tip seal facing the end plate is smaller than that of a material of the portion of the outer circumferential tip seal facing the end plate, and one in which a linear expansion coefficient of a material of the portion of the inner circumferential tip seal facing the end plate is smaller than that of a material of the portion of the outer circumferential tip seal facing the end plate.
  • the present invention can contribute to improving the durability of the inner circumferential tip seal by any of these configurations.
  • each tip seal can be improved if the material of the inner circumferential tip seal satisfies one of the requirements above.
  • the heat resistant temperature of the outer circumferential tip seal can be kept to be a temperature equal to or lower than the central value of the temperature rise range, a less inexpensive material whose heat resistant temperature is not so high can be selected as the material for the outer circumferential tip seal.
  • the stepped portion be positioned in an outer circumferential side of the rotation angle corresponding to the central value of the temperature range within which the temperature of the wrap rises from the rotation angle at the outermost circumferential portion of the wrap to the rotation angle at the innermost circumferential portion of the wrap, and that the inner circumferential tip seal be formed from a coating of an abrasion-resistant material at least at a portion facing the end plate.
  • coating means a film provided on a surface of the base material of a tip seal by any method such as painting, plating, sputtering, chemical vapor deposition, and physical vapor deposition.
  • the coating can be constituted by one or more layers provided on the surface of the base material.
  • Abrasion resistance higher than that of the outer circumferential tip seal can be imparted to the inner circumferential tip seal by forming the inner circumferential tip seal from the coating at least at the portion facing the end plate. Therefore, necessary abrasion resistance can be achieved while holding down the material cost by forming the base material of the inner circumferential tip seal from the same material for the base material of the outer circumferential tip seal.
  • the abrasion resistance can be further improved by selecting such a material as the material for the coating.
  • the application of the coating can give a surface that is smoother than that of the base material, the coefficient of friction of the surface of the inner circumferential tip seal reduces.
  • the abrasion resistance can also be enhanced in that the abrasion loss is reduced.
  • the stepped portion be positioned in an outer circumferential side of the rotation angle corresponding to the central value of the temperature range within which the temperature of the wrap rises from the rotation angle at the outermost circumferential portion of the wrap to the rotation angle at the innermost circumferential portion of the wrap, and that a thickness dimension of the inner circumferential tip seal be greater than a thickness dimension of the outer circumferential tip seal.
  • the tip seals slide against the end plate while being pressed against it to be gradually abraded, they are replaced periodically.
  • the inner circumferential tip seal which is subjected to a large pressing load due to back pressure, is abraded more easily than the outer circumferential tip seal.
  • the inner circumferential tip seal if made thick, can leave a thickness sufficient for the seal even when greatly abraded. This can ensure the reliability of the tip seal as well as decreasing the frequency of the replacement.
  • the thickness of the outer circumferential tip seal can be kept sufficient for the seal, thereby holding down the cost.
  • the scroll compressor of the present invention includes a fixed scroll and an orbiting scroll, the fixed scroll and the orbiting scroll each having a spiral wrap configured to decrease in height from an outer circumferential side to an inner circumferential side via a stepped portion, and an end plate having a stepped wall being erected following the stepped portion of the counterpart wrap, in which a thickness dimension of an inner circumferential tip seal provided in an inner circumferential side of the stepped portion and lying between the wrap and the counterpart end plate is greater than a thickness dimension of an outer circumferential tip seal provided in an outer circumferential side of the stepped portion and lying between the wrap and the counterpart end plate.
  • the present invention also utilizes the fact that in a 3D-type scroll compressor, each tip seal is divided into portions on both sides of a step of a wrap.
  • the thickness of the inner circumferential tip seal is made greater than that of the outer circumferential tip seal.
  • the inner circumferential tip seal can leave a thickness sufficient for the seal. This improves the durability and the reliability of the tip seals.
  • the thickness of the outer circumferential tip seal can be kept sufficient for the seal, thereby holding down the cost.
  • the stepped portion is positioned within a rotation angle range exceeding 2 ⁇ in an inner circumferential side from the rotation angle at the outermost circumferential portion of the wrap.
  • the value 2 ⁇ corresponds to a rotation angle obtained by one revolution of the orbiting scroll. While the orbiting scroll makes one revolution, suction inlets open at the outermost circumferential portions of the wraps and then close again.
  • the length of the outer circumferential tip seal of 2 ⁇ or more can be assured. This can ensure the cost reduction effect by using an inexpensive material for the outer circumferential tip seal.
  • the stepped portion be positioned within a rotation angle range exceeding 3 ⁇ in an inner circumferential side from the rotation angle at the outermost circumferential portion of the wrap.
  • the stepped portion is positioned exceeding 3 ⁇ from the outermost circumferential portion, the stepped portion does not exist in compression chambers when the suction inlets are closed to close up the compression chambers, and the compression chambers would not decrease in volume in the height direction of the wrap. This can maximize the volume of the compression chambers positioned at the outermost circumferential portion, thereby ensuring a large compression ratio.
  • the scroll compressor of the present invention can compress any working fluid such as a refrigerant and air, but is especially preferably used in an air-compressing scroll compressor. If used for compressing air, the temperature rises significantly at the central portion of each scroll, and thus the present invention, which can impart durability to the inner circumferential tip seal, has a great effect.
  • the present invention can be applied to both a scroll compressor using an oil for seal, cooling, and lubrication of the scroll and a scroll compressor of an oil-free type not using oil, but is especially useful when applied to the oil-free type scroll compressor. This is because in the oil-free type scroll compressor, the tip seals slide directly against the end plate without an oil (lubricant), and thus the temperature rises significantly at the inner circumferential side.
  • the effect of the present invention is pronounced when the present invention is applied to an air-compressing, oil-free scroll compressor.
  • a 3D-type scroll compressor with improved reliability can be provided by improving the durability of a tip seal.
  • a scroll compressor 10 shown in FIG. 1 is suitably used for, for example, a brake or an air spring of a railroad car as a compressed air source.
  • the scroll compressor 10 includes a fixed scroll 20 fixed to a case (not shown), an orbiting scroll 30 which is caused to revolve with respect to the fixed scroll 20, and a motor 11 providing torque to the orbiting scroll 30.
  • the scroll compressor 10 draws air in between the fixed scroll 20 and the orbiting scroll 30 with the motor 11 as a power source and discharges air compressed at compression chambers S formed between the fixed scroll 20 and the orbiting scroll 30.
  • the scroll compressor 10 is an oil-free type compressor not using oil for seal, cooling, and lubrication of a scroll, unlike a conventional scroll compressor which compresses, together with air, oil for seal, cooling, and lubrication of a scroll.
  • the scroll compressor 10 is accommodated in a case (not shown) together with a fan for cooling the motor 11 or a bearing, a device for cooling and dehumidifying compressed air to be discharged, and an electric box.
  • grease is used for the lubrication of the motor 11 or the bearing.
  • the motor 11 is configured to include a stator and a rotor accommodated in a motor case 12.
  • the motor 11 outputs a torque by energizing the stator and rotating the rotor.
  • the torque is transmitted to a shaft 15 that is coupled by a coupling 14 to an output shaft 13 provided to the rotor.
  • the shaft 15 is provided at its end portion with an eccentric pin 151 that is eccentric with respect to the shaft center.
  • the fixed scroll 20 includes a fixed end plate 200 and a spiral wrap 21 erected on one surface side of the fixed end plate 200.
  • the orbiting scroll 30 also includes an orbiting end plate 300 and a spiral wrap 31 erected on one surface side of the orbiting end plate 300.
  • the fixed scroll 20 and the orbiting scroll 30 are formed from a metal such as aluminum, an aluminum alloy, and iron (e.g., cast iron or steel). Surfaces of the fixed scroll 20 and the orbiting scroll 30 may be subjected to a surface treatment such as alumite treatment if the scrolls are of an aluminium based material, or quenching and tempering, nitriding, and carburization if the scrolls are of an iron/steel material.
  • a surface treatment such as alumite treatment if the scrolls are of an aluminium based material, or quenching and tempering, nitriding, and carburization if the scrolls are of an iron/steel material.
  • the orbiting scroll 30 is coupled to the above eccentric pin 151 by a boss 34 provided on a back surface of the orbiting end plate 300.
  • the orbiting scroll 30 is caused to revolve with respect to the shaft center of the shaft 15 while being prevented from rotating by an Oldham ring (not shown).
  • the wrap 21 of the fixed scroll 20 and the wrap 31 of the orbiting scroll 30 are off-centered from each other by a predetermined amount, and intermeshed out of phase with each other by 180 degrees.
  • the compression chambers S are formed point-symmetrically to the central portions (the innermost circumferential portions) of the spirals of the wraps 21 and 31 between the fixed scroll 20 and the orbiting scroll 30.
  • a suction inlet IN of air is formed between an end portion at an outermost circumferential portion of the wrap 21 and the wrap 31 and also between an end portion at an outermost circumferential portion of the wrap 31 and the wrap 21.
  • the compression chambers S are formed that are filled with the air drawn through the suction inlets IN.
  • the compression chambers S are gradually forced to an inner circumferential side while decreasing the volume, with the revolution of the orbiting scroll 30.
  • the air inside the compression chambers S is discharged through a discharge port 201 ( FIG. 1 ) formed at the central portion of the spiral on the fixed end plate 200.
  • the scroll compressor 10 is a 3D-type scroll compressor, and the volumes of the compression chambers S formed between the both scrolls 20 and 30 decrease also in the height direction of the wraps 21 and 31 in the middle of the spiral.
  • the height of the wraps 21 and 31 is lower at the inner circumferential side than at the outer circumferential side and the counterpart end plates 300 and 200 that respectively face the wraps 21 and 31 are projected toward the inside more at the inner circumferential side than at the outer circumferential side as shown in FIG. 3 .
  • the wraps 21 and 31 respectively have stepped portions 21C and 31C that become lower from the outer circumferential side to the inner circumferential side
  • the end plates 300 and 200 respectively have stepped walls 20C and 30C that become taller from the outer circumferential side to the inner circumferential side.
  • the stepped walls 20C and 30C are respectively formed in an arc shape in a plan view of the end plates 200 and 300.
  • the wrap 21 of the fixed scroll 20 is divided into an inner circumferential wrap 21A positioned in an inner circumferential side of the stepped portion 21C and an outer circumferential wrap 21B positioned in an outer circumferential side of the stepped portion 21C.
  • a bottom of the orbiting end plate 300 facing the wrap 21 is segmented into an inner circumferential bottom 30A and an outer circumferential bottom 30B at the stepped wall 30C.
  • the wrap 31 of the orbiting scroll 30 is divided into an inner circumferential wrap 31A positioned in an inner circumferential side of the stepped portion 31C and an outer circumferential wrap 31B positioned in an outer circumferential of the stepped portion 31C.
  • a bottom of the fixed end plate 200 facing the wrap 31 is segmented into an inner circumferential bottom 20A and an outer circumferential bottom 20B at the stepped wall 20C.
  • the inner circumferential wrap 21A of the fixed scroll 20 has an inner circumferential tip seal 41 at its tip.
  • the inner circumferential tip seal 41 lies between the inner circumferential wrap 21A and the inner circumferential bottom 30A of the orbiting end plate 300.
  • the inner circumferential tip seal 41 is provided along almost the entire length of the inner circumferential wrap 21A from a starting end of the inner circumferential wrap 21A positioned close to the stepped portion 21C to a terminal end of the inner circumferential wrap 21A positioned at the central portion of the spiral.
  • the outer circumferential wrap 21B of the fixed scroll 20 has an outer circumferential tip seal 42 at its tip.
  • the outer circumferential tip seal 42 lies between the outer circumferential wrap 21B and the outer circumferential bottom 30B of the orbiting end plate 300.
  • the outer circumferential tip seal 42 is provided along almost the entire length of the outer circumferential wrap 21B from a starting end of the outer circumferential wrap 21B positioned at an outermost circumferential portion of the spiral to a terminal end of the outer circumferential wrap 21B positioned close to the stepped portion 21C.
  • the inner circumferential tip seal 41 and the outer circumferential tip seal 42 are formed to have the same thickness.
  • the inner circumferential wrap 31A also has an inner circumferential tip seal 51 at its tip.
  • the inner circumferential tip seal 51 lies between the inner circumferential wrap 31A and the inner circumferential bottom 20A of the fixed end plate 200.
  • the inner circumferential tip seal 51 is formed similarly to the inner circumferential tip seal 41.
  • the outer circumferential wrap 31B has an outer circumferential tip seal 52 at its tip.
  • the outer circumferential tip seal 52 lies between the outer circumferential wrap 31B and the outer circumferential bottom 20B of the fixed end plate 200.
  • the outer circumferential tip seal 52 is formed similarly to the outer circumferential tip seal 42.
  • tip seals 41, 42, 51, and 52 are accommodated in their respective seal grooves D formed in the wraps into which the tip seals are provided as shown in FIG. 4 .
  • compressed air is introduced through a gap G between an inner wall of the seal groove D positioned at the inner circumferential side and the tip seal, along the seal groove D to a back surface side of the tip seal. This causes a negative pressure at the surface side of the tip seal relative to the back surface side to lift the tip seal from the seal groove D, thereby pressing the tip seal against the end plate. Then, a clearance between the tip seal and the end plate is sealed, thereby keeping the compression chambers S airtight.
  • a material of the inner circumferential tip seals 41 and 51 and a material of the outer circumferential tip seals 42 and 52 are different from each other.
  • the material of the inner circumferential tip seals 41 and 51 and the material of the outer circumferential tip seals 42 and 52 are determined based on the temperature and the pressure which rise with the compression of air.
  • FIG. 5 shows how the temperature of the wraps 21 and 31 rises with proximity to the central portion (the innermost circumferential portion) from the outermost circumferential portion (0 rad) of the spiral.
  • the rotation angle from 0 rad to 2 ⁇ rad corresponds to a rotation angle from the opening to the close of the suction inlets IN.
  • the inside of the compression chambers S is under the atmosphere outside the scrolls 20 and 30, and thus the temperature hardly rises.
  • the temperature of the wraps 21 and 31 from the outermost circumferential portion to 2 ⁇ rad does not increase beyond about 50°C.
  • the temperature shown in FIG. 5 is just an example.
  • the temperature and the slope of the temperature rise change in accordance with the volume and the compression ratio of the compression chambers S, and the rotation angle from the outermost circumferential portion to the innermost circumferential portion of the wraps 21 and 31. In any case, the temperature similarly rises slowly from the outermost circumferential portion to 2 ⁇ and rises gradually after exceeding 2 ⁇ toward the central portion.
  • the inner circumferential tip seals 41 and 51 disposed at the inner circumferential sides of the wraps 21 and 31 including the central portions of the spirals are required to have heat resistance to withstand high temperatures as above.
  • the inner circumferential tip seals 41 and 51 are subjected to high back pressure due to the compressed air compared with the outer circumferential tip seals 42 and 52. As a result, the inner circumferential tip seals 41 and 51 slide while being strongly pressed against the end plates, resulting in a large frictional force between the inner circumferential tip seals 41 and 51 and the end plates. Accordingly, in order to avoid early wear of the inner circumferential tip seals 41 and 51 due to the friction, the inner circumferential tip seals 41 and 51 are also required to have abrasion resistance.
  • the inner circumferential tip seals 41 and 51 are disposed at the inner circumferential sides which reach high temperatures and frictional heat acts between the inner circumferential tip seals 41 and 51 and the end plates, the inner circumferential tip seals 41 and 51 undergo a large amount of thermal expansion. Thus, the inner circumferential tip seals 41 and 51 are abraded significantly when pressed against the end plates more strongly. In order to reduce the abrasion loss, it is desirable that the inner circumferential tip seals 41 and 51 have a small linear expansion coefficient.
  • the material for the inner circumferential tip seals 41 and 51 is selected from resins and metals satisfying the heat resistance and the abrasion resistance under the conditions of high temperatures and high pressures as described above.
  • Resins which may be used for the inner circumferential tip seals 41 and 51 include PI (polyimide), PEEK (polyether ether ketone), and PTFE (polytetrafluoroethylene).
  • PI polyimide
  • PEEK polyether ether ketone
  • PTFE polytetrafluoroethylene
  • PAI polyamide imide
  • PPS polyphenylene sulfide
  • Fillers such as a metal or carbon may be mixed in these resins.
  • the inner circumferential tip seals 41 and 51 may be formed by, for example, injection molding from the resins as described above.
  • the inner circumferential tip seals 41 and 51 may also be formed by, for example, press blanking from a metal like iron.
  • respective materials of the inner circumferential tip seals 41 and 51 may be different from each other. The same applies to the outer circumferential tip seals 42 and 52.
  • the heat resistance and the abrasion resistance required for the inner circumferential tip seals 41 and 51 vary in accordance with the temperature and the pressure at the central portion of the spiral.
  • the inner circumferential tip seals 41 and 51 preferably have a heat resistant temperature of 240°C or more.
  • the outer circumferential tip seals 42 and 52 which are disposed at the outer circumferential sides of the wraps 21 and 31 including the outermost circumferential portions at which air is drawn, rise in temperature by a small amount and are subjected to a smaller back pressure than at the inner circumferential sides, resulting in a small pressing load. Accordingly, the outer circumferential tip seals 42 and 52 may have a smaller heat resistance and abrasion resistance and a higher linear expansion coefficient than those of the inner circumferential tip seals 41 and 51.
  • Resins which may be used for the outer circumferential tip seals 42 and 52 include PAI (polyamide imide), PPS (polyphenylene sulfide), and PA (polyamide).
  • PAI polyamide imide
  • PPS polyphenylene sulfide
  • PA polyamide
  • Other resins such as PTFE (polytetrafluoroethylene) may also be adopted.
  • the outer circumferential tip seals 42 and 52 may also be formed from a metal like iron.
  • the inner circumferential tip seals 41 and 51 are formed from a material satisfying at least one requirement of a higher heat resistant temperature, a smaller comparative abrasion quantity, and a smaller linear expansion coefficient than those of the material of the outer circumferential tip seals 42 and 52, as long as the materials satisfy the heat resistances, the abrasion resistances required for the inner circumferential tip seals 41 and 51 and the outer circumferential tip seals 42 and 52 and their balance of thermal expansion.
  • the inner circumferential tip seals 41 and 51 and the outer circumferential tip seals 42 and 52 may be formed from materials having comparable heat resistant temperatures and different comparative abrasion quantities or linear expansion coefficients.
  • they may be formed from materials having comparable comparative abrasion quantities and different heat resistant temperatures or linear expansion coefficients, or may be formed from materials having comparable linear expansion coefficients and different heat resistant temperatures or comparative abrasion quantities.
  • the outer circumferential tip seals 42 and 52 are formed from a material less expensive than that of the inner circumferential tip seals 41 and 51 as long as the inner circumferential tip seals 41 and 51 have durability necessary for the high temperature and the high pressure at the central portion of the spiral and the outer circumferential tip seals 42 and 52 satisfy a necessary heat resistance and abrasion resistance.
  • positions of the stepped portions 21C and 31C separating the inner circumferential tip seals 41 and 51 from the outer circumferential tip seals 42 and 52 are set for achieving improved durability and reduced cost of the tip seal in a well-balanced manner.
  • the positions of the stepped portions 21C and 31C mean sites at which the outer circumferential wrap 21B erects from the inner circumferential wrap 21A.
  • a first index is an angle corresponding to the central value of a temperature range within which the temperatures of wraps 21 and 31 rise.
  • a second index is a rotation angle of 2 ⁇ rad, which is obtained by one revolution of the orbiting scroll 30.
  • the temperature range of the wraps 21 and 31 ranges from 25°C at 0 rad to 225°C at about 7 ⁇ rad with the central value at 125°C.
  • the rotation angle corresponding to the central value at 125°C is 4 ⁇ rad (the first index).
  • the rotation angle of 2 ⁇ rad (the second index) corresponding to one revolution corresponds to the rotation angle from the opening to the close of the suction inlets IN at the outermost circumferential portions of the wraps 21 and 31.
  • the value 2 ⁇ rad is used to ensure the cost reduction effect obtained by selecting an inexpensive material for the outer circumferential tip seals 42 and 52.
  • the positions of the stepped portions 21C and 31C are each preferably set within a range of 2 ⁇ rad or more and 4 ⁇ rad or less in the inner circumferential sides from the outermost circumferential portions of the wraps 21 and 31.
  • the heat resistant temperature of the outer circumferential tip seals 42 and 52 can be kept to temperatures equal to or lower than the central value of the temperature rise range.
  • the length of the outer circumferential tip seals 42 and 52 of 2 ⁇ rad or more can be assured. This can ensure the cost reduction effect by selecting an inexpensive material for the outer circumferential tip seals 42 and 52.
  • the positions of the stepped portions 21C and 31C are set at 2 ⁇ in the present embodiment, but the stepped portions 21C and 31C may be provided at any position in a range of 2 ⁇ rad or more and 4 ⁇ rad or less from the outermost circumferential portions of the wraps 21 and 31.
  • the stepped portions 21C and 31C are positioned 3 ⁇ rad or more in the inner circumferential sides from the outermost circumferential portions, the stepped portions 21C and 31C do not exist in the compression chambers S when the suction inlets IN are closed to close up the compression chambers S.
  • the compression chambers S each form a space having a uniform dimension between the end plates 200 and 300 with no volume reduction in the height direction of the wraps 21 and 31. This can maximize the volume of the compression chambers S positioned in the outermost circumferential portions, thereby ensuring a large compression ratio.
  • the inner circumferential tip seals 41 and 51 and the outer circumferential tip seals 42 and 52 set apart and separated by the stepped portions 21C and 31C of the wraps 21 and 31, the inner circumferential tip seals 41 and 51 are formed from a material determined by the high temperature and high pressure at the central portions of the spirals, while the outer circumferential tip seals 42 and 52 are formed from an inexpensive material.
  • the wraps 21 and 31 and the end plates 300 and 200 can be kept sealed therebetween without causing erosion, an abnormal abrasion, or a seizure to the tip seals, thereby ensuring the reliability of the scroll compressor 10 as well as contributing to cost reduction.
  • the second embodiment will be described mainly focusing on points different from those in the first embodiment. Configurations similar to those in the first embodiment will be given the same characters.
  • the inner circumferential tip seals 41 and 51 are coated with an abrasion-resistant material instead of differentiating the materials between the inner circumferential tip seals 41 and 51 and the outer circumferential tip seals 42 and 52.
  • the inner circumferential tip seal 41 has an abrasion resistant coating 45 on a surface.
  • a material of the coating 45 to be used include PTFE (polytetrafluoroethylene), PEEK (polyether ether ketone), DLC (diamond-like carbon), TiN (titanium nitride), and CrN (chromium nitride).
  • the abrasion resistance of the coating 45 is determined as appropriate according to the pressure at the central portion of the spiral.
  • a film thickness of the coating 45 may be set according to the comparative abrasion quantity required for the coating 45.
  • the coating 45 at least forms a surface 45S (surface) facing the inner circumferential bottom 30A of the end plate 300, and faces the counterpart end plate 300.
  • the material of the portion of the inner circumferential tip seal 41 facing the end plate 300 (coating 45) is different from that of the portion of the outer circumferential tip seal 42 without a coating facing the end plate 300.
  • the inner circumferential tip seal 51 may be provided with a coating 45 similar to that of the inner circumferential tip seal 41.
  • a coating 45 of PTFE or PEEK may be formed by spraying and applying a liquid material prepared by mixing resin powder into a solution onto the inner circumferential tip seals 41 and 51 (base material) with an air spray gun and then heating the applied liquid material at a melting point of the resin or higher to fuse it with the inner circumferential tip seals 41 and 51.
  • the liquid material is repeatedly applied and heated until a predetermined film thickness is obtained.
  • an electrostatic powder coating method of applying resin powder to a base material using static electricity, a dip method, and the like may be used. In any case, resin is fused with a base material by applying heat.
  • a coating 45 of DLC may be formed by plasma-enhanced chemical vapor deposition (PECVD) or physical vapor deposition (PVD).
  • PECVD plasma-enhanced chemical vapor deposition
  • PVD physical vapor deposition
  • a coating 45 of TiN or CrN may be formed by PVD.
  • the material for the base materials for the inner circumferential tip seals 41 and 51 on which the coating 45 is formed one that does not melt by heat applied during the process of forming the coating 45 is selected.
  • the base materials of the inner circumferential tip seals 41 and 51 may be made of the same material as that of the outer circumferential tip seals 42 and 52.
  • abrasion resistance higher than that of the outer circumferential tip seals 42 and 52 can be imparted to the inner circumferential tip seals 41 and 51 by applying the coating 45 to the inner circumferential tip seals 41 and 51. Therefore, necessary abrasion resistance can be achieved while holding down the material cost by forming the base material of the inner circumferential tip seals 41 and 51 from the same material as that of the outer circumferential tip seals 42 and 52.
  • abrasion resistance can be further improved by selecting such a material as the material for the coating 45.
  • the coefficient of friction of the surfaces of the inner circumferential tip seals 41 and 51 reduces.
  • DLC has a coefficient of friction of about 0.1 (dry condition), for example.
  • the abrasion resistance can be increased also in that the abrasion loss reduces due to the small coefficient of friction.
  • the base materials of the inner circumferential tip seals 41 and 51 may be formed from a material different from that of the outer circumferential tip seals 42 and 52.
  • the third embodiment will be described also mainly focusing on points different from those in the first embodiment, and configurations similar to those already described will be given the same characters.
  • the inner circumferential tip seals and the outer circumferential tip seals are different in thickness.
  • the inner circumferential tip seals and the outer circumferential tip seals are the same in material.
  • the inner circumferential tip seal 61 provided to the inner circumferential wrap 21A and the outer circumferential tip seal 42 provided to the outer circumferential wrap 21B are different in thickness. It is to be noted that the inner circumferential tip seal provided to the inner circumferential wrap 31A is formed similarly to the inner circumferential tip seal 61, and the outer circumferential tip seal provided to the outer circumferential wrap 31B is formed similarly to the outer circumferential tip seal 42.
  • a thickness of the outer circumferential tip seal 42 is set to T1 in the depth direction of the seal groove D. This thickness is the same as that of the outer circumferential tip seal 42 in the first and second embodiments.
  • a thickness T2 of the inner circumferential tip seal 61 is larger than the thickness T1 of the outer circumferential tip seal 42.
  • the inner circumferential tip seal 61 if made thick, can leave a thickness sufficient for the seal even when greatly abraded. This ensures the reliability of the tip seal.
  • the thickness T1 of the outer circumferential tip seal 42 can be kept sufficient for the seal, thereby holding down the cost.
  • the third embodiment may be combined with the first or second embodiment. That is, in the third embodiment, the inner circumferential tip seals 41 and 51 may be formed from a material different from that of the outer circumferential tip seals 42 and 52, or the inner circumferential tip seals 41 and 51 may be provided with the coating 45.
  • durability to withstand the high temperature and high pressure at the inner circumferential side of the wraps can be imparted to the inner circumferential tip seals, thereby improving the reliability of the scroll compressor.
  • the temperature and the compression ratio may become as high as those in air-compressing scroll compressors at the central portions of the spirals.
  • the present invention has a great effect even in such a case.
  • the effect of the present invention is also pronounced in oil-free scroll compressors that compress a refrigerant like that.
  • the stepped portion is provided only at one site in a circumferential direction of each wrap in the scroll compressors of the first to third embodiments, the stepped portions may be provided at a plurality of sites in the circumferential direction of the wrap.
  • stepped portions 211 and 212 are provided at two sites in the circumferential direction of the wrap 21 as shown in FIG. 8 , there exist an innermost circumferential tip seal 71 provided at a position including the innermost circumferential portion (the central portion of the spiral), an outermost circumferential tip seal 73 provided at a position including the outermost circumferential portion, and an intermediate tip seal 72 provided at an intermediate position.
  • first stepped portion 211 when one of the two stepped portions 211 and 212 that is positioned at the outer circumferential side is called a first stepped portion 211 and one positioned at the inner circumferential side is called a second stepped portion 212, the intermediate tip seal 72 and the innermost circumferential tip seal 71 positioned in the inner circumferential side of the first stepped portion 211 and the outermost circumferential tip seal 73 positioned in the outer circumferential side of the first stepped portion 211 may be different in material or thickness, based on the first stepped portion 211.
  • the innermost circumferential tip seal 71 positioned in the inner circumferential side of the second stepped portion 212 and the intermediate tip seal 72 and the outermost circumferential tip seal 73 positioned in the outer circumferential side of the second stepped portion 212 may be different in material or thickness, based on the second stepped portion 212.
  • outermost circumferential tip seal 73, the intermediate tip seal 72, and the innermost circumferential tip seal 71 may be different stepwise in material or thickness.
  • the intermediate tip seal 72 positioned in the inner circumferential side of the first stepped portion 211 and the outermost circumferential tip seal 73 positioned in the outer circumferential side of the first stepped portion 211 may be different in material or thickness and at the same time the innermost circumferential tip seal 71 positioned in the inner circumferential side of the second stepped portion 212 and the intermediate tip seal 72 positioned in the outer circumferential side of the second stepped portion 212 may be different in material or thickness.
  • the temperature and the pressure of the gas rise from the outermost circumferential portion toward the innermost circumferential portion of each wrap, the temperature and the pressure become higher at more inward portions. Therefore, it may be configured such that the material of the inner circumferential tip seals positioned relatively more inwardly is more excellent in heat resistance and abrasion resistance than the material of the outer circumferential tip seals positioned relatively outwardly and that the inner circumferential tip seal is thicker than the outer circumferential tip seal.
  • the scroll compressor of the present invention is not limited to one powered by motor torque, and may be powered by a driving force transmitted from an engine through a belt to the shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (7)

  1. Compresseur à spirales (10) comportant une spirale fixe (20) et une spirale à mouvement orbital (30), la spirale fixe (20) et la spirale à mouvement orbital (30) comprenant chacune
    un enroulement en spirale (21, 31) configuré pour diminuer en hauteur depuis un côté circonférentiel extérieur (21B, 31B) jusqu'à un côté circonférentiel intérieur (21A, 31A) en passant par une partie étagée (21C, 31C) et
    une plaque d'extrémité (200, 300) ayant une paroi étagée (20C, 30C) qui se dresse à la suite de la partie étagée (21C, 31C) de l'enroulement associé (21, 31),
    caractérisé en ce que
    un joint d'extrémité circonférentielle intérieure (51) prévu dans un côté circonférentiel intérieur de la partie étagée (21C, 31C) et se trouvant entre l'enroulement (21, 31) et la plaque d'extrémité associée (200, 300) et un joint d'extrémité circonférentielle extérieure (52) prévu dans un côté circonférentiel extérieur de la partie étagée (21C, 31C) et se trouvant entre l'enroulement (21, 31) et la plaque d'extrémité associée (200, 300) sont différents sur le plan de la matière au moins au niveau de parties faisant face à la plaque d'extrémité (200, 300) ; et
    la partie étagée (21C, 31C) est positionnée dans un côté circonférentiel extérieur d'un angle de rotation correspondant à une valeur centrale d'une plage de température dans laquelle une température de l'enroulement (21, 31) augmente, et dans une plage d'angle de rotation dépassant 2π dans un côté circonférentiel intérieur à partir d'un angle de rotation au niveau d'une partie circonférentielle extérieure de l'enroulement (21, 31).
  2. Compresseur à spirales (10) selon la revendication 1, dans lequel
    la partie étagée (21C, 31C) est positionnée dans le côté circonférentiel extérieur de l'angle de rotation correspondant à la valeur centrale de la plage de températures dans laquelle la température de l'enroulement (21, 31) s'élève depuis l'angle de rotation au niveau de la partie circonférentielle extérieure de l'enroulement (21, 31) jusqu'à un angle de rotation au niveau d'une partie circonférentielle la plus à l'intérieur de l'enroulement (21, 31), et
    le joint d'extrémité circonférentielle intérieure (51) est formé dans une matière répondant au moins à une exigence d'une température de résistance à la chaleur plus élevée, d'une plus faible quantité d'abrasion comparative, et d'un plus petit coefficient linéaire d'expansion que ceux d'une matière du joint d'extrémité circonférentielle extérieure (52).
  3. Compresseur à spirales (10) selon la revendication 1 ou 2, dans lequel
    la partie étagée (21C, 31C) est positionnée dans le côté circonférentiel extérieur de l'angle de rotation correspondant à la valeur centrale de la plage de températures dans laquelle la température de l'enroulement (21, 31) s'élève depuis l'angle de rotation au niveau de la partie circonférentielle extérieure de l'enroulement (21, 31) jusqu'à un angle de rotation au niveau d'une partie circonférentielle la plus à l'intérieur de l'enroulement (21, 31), et
    le joint d'extrémité circonférentielle intérieure (51) est formé à partir d'un revêtement d'une matière résistant à l'abrasion au moins au niveau d'une partie du joint d'extrémité circonférentielle intérieure (51) faisant face à la plaque d'extrémité (200, 300).
  4. Compresseur à spirales (10) selon l'une quelconque des revendications 1 à 3, dans lequel
    la partie étagée (21C, 31C) est positionnée dans le côté circonférentiel extérieur de l'angle de rotation correspondant à la valeur centrale de la plage de températures dans laquelle la température de l'enroulement (21, 31) s'élève depuis l'angle de rotation au niveau de la partie circonférentielle extérieure de l'enroulement (21, 31) jusqu'à un angle de rotation au niveau d'une partie circonférentielle la plus à l'intérieur de l'enroulement (21, 31), et
    une dimension d'épaisseur du joint d'extrémité circonférentielle intérieure (51) est plus grande qu'une dimension d'épaisseur du joint d'extrémité circonférentielle extérieure (52).
  5. Compresseur à spirales (10) comportant une spirale fixe (20) et une spirale à mouvement orbital (30), la spirale fixe (20) et la spirale à mouvement orbital (30) comprenant chacune
    un enroulement en spirale (21, 31) configuré pour diminuer en hauteur depuis un côté circonférentiel extérieur (21B, 31B) jusqu'à un côté circonférentiel intérieur (21A, 31A) en passant par une partie étagée (21C, 31C) et
    une plaque d'extrémité (200, 300) ayant une paroi étagée (20C, 30C) qui se dresse à la suite de la partie étagée (21C, 31C) de l'enroulement associé (21, 31),
    caractérisé en ce que
    une dimension d'épaisseur d'un joint d'extrémité circonférentielle intérieure (51) prévu dans un côté circonférentiel intérieur de la partie étagée (21C, 31C) et se trouvant entre l'enroulement (21, 31) et la plaque d'extrémité associée (200, 300) est plus grande qu'une dimension d'épaisseur d'un joint d'extrémité circonférentielle extérieure (52) prévu dans un côté circonférentiel extérieur de la partie étagée (21C, 31C) et se trouvant entre l'enroulement (21, 31) et la plaque d'extrémité associée (200, 300) ; et
    la partie étagée (21C, 31C) est positionnée dans un côté circonférentiel extérieur d'un angle de rotation correspondant à une valeur centrale d'une plage de température dans laquelle une température de l'enroulement (21, 31) augmente, et dans une plage d'angle de rotation dépassant 2π dans un côté circonférentiel intérieur à partir d'un angle de rotation au niveau d'une partie circonférentielle extérieure de l'enroulement (21, 31).
  6. Compresseur à spirales (10) selon l'une quelconque des revendications 1 à 5, dans lequel
    de l'air est comprimé par la spirale fixe (20) et la spirale à mouvement orbital (30).
  7. Compresseur à spirales (10) selon l'une quelconque des revendications 1 à 6, dans lequel
    le joint d'extrémité circonférentielle intérieure (51) et le joint d'extrémité circonférentielle extérieure (52) glissent directement contre la plaque d'extrémité (200, 300) sans lubrifiant.
EP14830230.0A 2013-07-25 2014-06-24 Compresseur à volute Active EP2998585B1 (fr)

Applications Claiming Priority (2)

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JP2013154204A JP6214954B2 (ja) 2013-07-25 2013-07-25 スクロール圧縮機
PCT/JP2014/003372 WO2015011875A1 (fr) 2013-07-25 2014-06-24 Compresseur à volute

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EP2998585A1 EP2998585A1 (fr) 2016-03-23
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EP2998585B1 true EP2998585B1 (fr) 2017-04-26

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KR20170138506A (ko) * 2015-04-23 2017-12-15 에머슨 클라이미트 테크놀로지스 (쑤저우) 코., 엘티디. 스크롤 압축기 및 스크롤 압축기를 위한 구동 샤프트 및 언로딩 부시
SG11201801353VA (en) * 2015-08-25 2018-03-28 Murata Machinery Ltd Purge device, purge stocker, and purge method
CN110073106B (zh) * 2016-12-28 2022-01-28 纳博特斯克有限公司 涡旋式流体机械和车辆
JP2019073988A (ja) * 2017-10-12 2019-05-16 アネスト岩田株式会社 スクロール流体機械ユニット
EP4032764A1 (fr) * 2021-01-25 2022-07-27 ZF CV Systems Global GmbH Alimentation centrale en air

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Publication number Priority date Publication date Assignee Title
JPH0717762Y2 (ja) 1989-03-27 1995-04-26 岩田塗装機工業株式会社 スクロール流体機械
JPH06323101A (ja) * 1993-05-12 1994-11-22 Daikin Ind Ltd スクロール流体機械
JP3195994B2 (ja) * 1993-12-09 2001-08-06 株式会社日立製作所 スクロール流体機械
JP2003106269A (ja) * 2001-09-28 2003-04-09 Anest Iwata Corp スクロール流体機械
JP4395325B2 (ja) * 2003-05-21 2010-01-06 三菱重工業株式会社 段付き構造スクロール流体機械
JP4814189B2 (ja) * 2007-09-21 2011-11-16 三菱重工業株式会社 スクロール圧縮機
JP2010275895A (ja) * 2009-05-27 2010-12-09 Mitsubishi Heavy Ind Ltd スクロール圧縮機
GB2472637B (en) * 2009-08-14 2015-11-25 Edwards Ltd Scroll Compressor With Plural Sealing Types
JP5773615B2 (ja) 2009-12-15 2015-09-02 三菱重工業株式会社 スクロール圧縮機
JP2013160147A (ja) * 2012-02-06 2013-08-19 Mitsubishi Heavy Ind Ltd スクロール型圧縮機

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EP2998585A4 (fr) 2016-07-20
WO2015011875A1 (fr) 2015-01-29
EP2998585A1 (fr) 2016-03-23
JP6214954B2 (ja) 2017-10-18
JP2015025387A (ja) 2015-02-05

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