EP0854289A1 - Spiralverdrängungsanlage - Google Patents

Spiralverdrängungsanlage Download PDF

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Publication number
EP0854289A1
EP0854289A1 EP97100864A EP97100864A EP0854289A1 EP 0854289 A1 EP0854289 A1 EP 0854289A1 EP 97100864 A EP97100864 A EP 97100864A EP 97100864 A EP97100864 A EP 97100864A EP 0854289 A1 EP0854289 A1 EP 0854289A1
Authority
EP
European Patent Office
Prior art keywords
scroll
seal
housing
compressed fluid
driven
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Withdrawn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
EP97100864A
Other languages
English (en)
French (fr)
Inventor
Toshihiro Honma
Masaki Tsuji
Toru Sato
Shinji Kawazoe
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.)
Anest Iwata Corp
Original Assignee
Anest Iwata Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Anest Iwata Corp filed Critical Anest Iwata Corp
Priority to EP97100864A priority Critical patent/EP0854289A1/de
Publication of EP0854289A1 publication Critical patent/EP0854289A1/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Withdrawn legal-status Critical Current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
    • F04C18/02—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
    • F04C18/023—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 both members are 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure

Definitions

  • This invention relates to scroll fluid apparatuses and, more particularly, to a shaft seal structure in scroll fluid apparatus of rotating drive/driven scroll type comprising a drive and a driven scroll, the shaft seal structure being provided in a discharge part for discharging compressed fluid, as well as a scroll fluid apparatus, in which the engagement between laps and opposed scroll plate is adjustable.
  • Fig. 11 shows a prior art scroll fluid apparatus.
  • the apparatus comprises a stationary scroll 110 secured to an end face of a frame 140.
  • the stationary scroll 110 has vertically an involute lap 113 which is provided in a concave space defined by a peripheral wall 111 with a suction port 116 formed therein, and also has a discharge port 117 provided substantially at a central position for discharging compressed fluid.
  • a revolving scroll 120 In a concave space defined by the frame 140, a revolving scroll 120 is accommodated, which has an involute lap 121 formed vertically on a scroll body having an end surface in contact with an end surface of the peripheral wall 111.
  • the involute lap 121 has substantially the same shape as the lap 113 of the stationary scroll 110.
  • the laps 113 and 121 are engaged with each other in a 180-degree out-of-phase relation to each other.
  • Self-lubricating seals 131 are each fitted in a concave groove formed in the end surface of each of the laps 113 and 121 of the scrolls 110 and 120 in contact with the other scroll.
  • the laps 113 and 121 thus undergo sliding by lubricant-free oil.
  • a ring-like self-lubricant free seal 132 is fitted in a concave groove formed in the end surface of the stationary scroll 110 in contact with the corresponding end surface of the revolving scroll 120, whereby the concave space defined by the peripheral wall 111 noted above is thus sealed gas-tight from the outside.
  • the frame 140 axially supports a drive crankshaft 141 with a pulley 142 provided at one end, and also supports three driven crankshafts 150 spaced apart at an interval of 120° with respect to the main drive shaft 141.
  • crankshafts 141 and 150 have their eccentric end portions 411 and 501 supported for rotation via bearings 143 and 155 in an inner frame 125 which is integral with the revolving scroll 120.
  • Rotation of the drive crankshaft 141 causes revolving of the driven crankshafts 150 in correspondence to the eccentricity of the drive crankshaft 141, whereby the revolving scroll 120 undergoes revolving about the lap center of the stationary scroll 110 with a predetermined radius of revolving while not in rotation.
  • the parallelness and clearance of the revolving scroll 120 with respect to the stationary scroll 110 should be accurately adjusted so that the revolving scroll 120 can revolve with adequate accuracy of lap engagement. Without these accurate adjustments, fluid may leak through sealed spaces. In addition, the laps and the opposed sliding surfaces may be brought into contact with one another, resulting in noise generation and abnormal wear. Moreover, partial contact of the laps is liable, thus increa"ing the drive power and reducing the durability of the bearings.
  • ball bearings 151 are fitted for movement in the thrust direction on the driven crankshafts 150, which are provided at an interval of 120° with respect to the drive crankshaft 141.
  • the position of the ball bearings 151 in the thrust direction is made adjustable by turning outside race retainers 160 on plus or minus, which are screwed on the driven crankshafts 150, in either direction.
  • the outside race retainers 160 slightly project from the end surface of the frame 140, and can be locked by lids 146.
  • the driven crankshafts 150 have their eccentric portions 501 supported via bearings 155 in the inner frame 125 integral with the revolving scroll 120.
  • the thrust displacement volume between the sliding surface 120a of the revolving scroll 120 and the flame end surface 140a is adjustable by turning the outside race retainer 160 on plus or minus.
  • the bearings 155 which are provided near the outer periphery of the revolving scroll 120, are advanced and retreated in the thrust direction by turning the outside race retainers 160 in either direction on plus or minus. Therefore, some of the bearings 155 may be advanced or retreated excessively, while the others are advanced or retreated insufficiently, resulting in an increase of the drive power due to partial contact of laps or durability reduction of the bearings.
  • Another object of the invention is to improve a shaft seal structure, which is provided in a discharge section for compressing and discharging fluid.
  • a scroll fluid apparatus of rotating drive/driven scroll type which comprises a drive scroll and a driven scroll plate, these scrolls being driven in a housing such that their laps compress fluid and discharge tee compressed fluid to the outside with their laps, and a scroll adjustment mechanism for adjusting the engagement between the laps and the opposed scroll plates.
  • the scroll fluid apparatus further comprises:
  • thrust displacement adjustment members In a scroll fluid apparatus of rotating drive/driven scroll type, a drive and a driven scroll plates are rotated around their supporting means. Therefore, where the thrust displacement adjustment is made outer peripheral portions of the scroll plates, thrust displacement adjustment members should be held in the housing over the entire circumference, and complicate the construction.
  • the scroll fluid apparatus of rotating drive/driven scroll type is comprising with the drive and driven scroll plates having their supporting means for supporting in the above housing at the neighborhood of central portions of their opposite side face to the lap formative face of each scroll plate, that is, the both scroll plates are supported at their central portion of each scroll plate by the housing.
  • the above supporting means are displaceable adjusted in the axial direction of scroll plate, instead of adjustable arranging the plural adjusting means provided in the outer peripheral portion of scroll plate.
  • the outer peripheral portion of the scroll plate is not in partial contact with the opposed scroll means and is not driven with squeak due to excessive displacement of the one of adjusting means in the above plurality, therefore it is possible to imp"ove the durability.
  • the outer peripheral potion of scroll plate are also displaceably adjusted. Therefore, it is not caused that the supporting means of the central portion are inclined diagonally to result in irrational friction between the supporting means and the housing portion supporting the above supporting means for the driving of the scroll plate, durability thus can be improved.
  • the position control with respect to a reference surface is allowed in a narrow range centered on the supporting means, compared to the case of adjustable arrangement a plural adjusting means provided on the outer peripheral portion of scroll plate. Thus, it is possible to reduce the steps of manufacture.
  • the supporting means are supported via the elastically displaceable means which is displaceably in axial di"ection
  • the supporting means can be secured to the housing by the above elastically displaceable member after the thrust displacement adjustment of the scroll plate in the axial direction.
  • a dust seal housing is provided, which supports the neighborhood of the outer periphery on the lap formative face side of each scroll plates.
  • the gap or distance between both scroll plates are defined by the dust seal housing and can be easily adjusted through thrust displacement adjustment of the supporting means in the central portion of the scroll plates.
  • the dust seal housing further positions outer peripheral portions of the both scroll plates to eliminate fabrication errors, thus eliminating axial deviations of the scroll outer peripheral portions during driving. It is thus possible to prevent otherwise possible vibrations and durability reduction.
  • a scroll fluid apparatus of rotating drive/driven scroll type which comprises a drive scroll and a driven scroll, these scrolls being driven in a housing such that their laps compress fluid and discharge the compressed fluid to the outside, an intermediate seal member having a compressed fluid passage being provided between a housing discharge opening for discharging compressed fluid to the outside of housing and a scroll plate discharge exit for discharging compressed fluid, said intermediate seal member having a one end portion capable of being displaced along the compressed fluid passage and in gas-tight contact with the scroll discharge exit, and the other end portion is provided being faced with the edge of the housing discharge opening; the other end portion of the intermediate seal member and the housing discharge opening edge being held in gas-tight contact with each other by the pressure of the compressed fluid.
  • an intermediate seal member i.e., a seal sleeve plate 101 and a seal plate 102
  • a discharge opening 12a through which compressed fluid in the housing is discharged
  • a discharge exit 14e through which compressed fluid in the scroll plates is discharged.
  • One end portion of the intermediate seal member is in gas-tight contact with the discharge exit 14e while being capable of being displaced along the compressed fluid passage.
  • the other end portion of the intermediate seal member faces the edge of the discharge opening 12a.
  • the pressure of the compress"d fluid serves as a sealing force to hold the other end portion (on the side of the seal plate 102) of the intermediate seal member and the discharge opening edge (i.e. the seal plate 102) in gas-tight contact with each other.
  • the compressed fluid passage and the cooling air circulation passage 10 are sealed in gas-tight each other, thus the compressed fluid to be discharged to the outside of the housing should be prevented from entering in a cooling air circulation passage 10a.
  • the discharge opening is provided in a seal retainer 103 capable of being detached in the member (the mounting member cover) 11, it is possible to replace the sleeve seal 101 or the seal plate 102 even though was worn, as desired.
  • the intermediate seal member may include a seal plate having a central opening, which is disposed on the discharge opening side for discharging compressed fluid to the outside of housing, and a sleeve seal which is disposed on the scroll plate compressed fluid discharge exit side, so that its discharge side of above intermediate seal member is in communication with the housing discharge opening for discharging compressed fluid.
  • At least either one of the contact surfaces of the seal plate and sleeve seal plate in contact with each other, may be a curved surface.
  • the sleeve seal plate may be made of a self-lubricating material.
  • the seal plate may be made of a highly wear-resistant material.
  • a scroll mounting member having an inner passage may be provided such that an end portion is connected to a compressed fluid discharge exit of the driven scroll, a sleeve seal made of a resin may be axially slidably fitted in an other end portion of the scroll mounting member, and a seal plate made of a wear-resistant material and having a central opening may be disposed in the discharge opening side of the housing surrounding the driven scroll such that it faces the above sleeve seal.
  • the one end of a sleeve seal made of a resin having a compressed fluid discharge passage may be axially slidably fitted in a discharge opening side recess for discharging the compressed fluid to the outside of the housing surrounding the driven scroll such that it faces the discharge opening, and a one end of scroll mounting member having an inner passage may be provided such that an end portion is connected to a compressed fluid discharge exit of the driven scroll, and that the other end of it is axially slidably fitted in the discharge passage of the sleeve seal via a seal plate made of a wear-resistant material and having a central opening may be axially slidably fitted in the discharge passage of the sleeve seal.
  • the sleeve seal may be made of a synthetic resin which has such a heat resistance that it can withstand an increased temperature due to heat of fluid compression, as well as a self-lubricating property of the sliding surface.
  • this means is constructed with an intermediate seal comprising a seal plate 102, which is disposed on the discharge opening side thereof for discharging compressed fluid to the outside of housing and having a central opening, and a sleeve seal 101 disposed in a scroll plate on the compressed fluid discharge exit side thereof, and where a seal retainer 103 detachably disposed in the mounting member cover 11, the above sleeve seal 101 is made of a self-l"bricating material and the above seal plate 102 is made of a highly wear-resistant material, by which it is possible to obtain lubrication-free operation of the sleeve seal 101 rotating with the driven scroll and readily replace the sleeve seal 101 as desired.
  • the two contact surfaces of the seal 102 and the sleeve seal 101 in contact with each other is formed as a curved surface, the two contact surfaces can readily become intimate due to a few contact surface each other, thus readily forming a gas-tight state of seal.
  • the sleeve seal 101 should be made of a heat-resistant material capable of withstanding the elevated temperature brought about by the heat of fluid compression.
  • the seal plate 102 is desirably secured to the seal retainer 103. This means that the seal plate is desirably made of a ceramic or like material, which has been surface treated and has a mirror-finished sliding surface.
  • a scroll mounting member 5 for mounting a drive scroll 13 to be described later, is secured to the left end of a drive shaft 18 which is coupled to a motor (not shown).
  • the scroll mounting member 5 is mushroom-like in shape and has a communication bore, which extends through a stem portion and a flaring portion of the member 5 and is fitted on the drive shaft 18, and it also has three radially spaced-apart mounting portions 5b formed on the outer side of the flaring portion, the mounting portions 5b having 3 holes 5a through which cooling air flows.
  • a rotary bearing 17 is fitted on the outer periphery of the flaring portion of the scroll mounting member 5.
  • the rotary bearing 17 has its outer periphery secured to a scroll housing 6, which is secured to a base 2.
  • the scroll mounting member 5 is disposed for rotation in the scroll housing 6 in a state secured to the drive shaft 18.
  • the scroll housing 6 has a plura"ity of holes 6a formed in its peripheral wall for discharging air having cooled the drive scroll 13.
  • the drive scroll 13 is disc-like and has fan blades 13c formed on its back side and an involute lap 13a formed on its front sliding surface 13d.
  • the lap 13a has a tip groove formed in its tip facing the opposed sliding surface, and a tip seal 21 of a self-lubricating material such as a fluorine-based resin is fitted in the tip groove.
  • the drive scroll 13 specifically has three fan blades formed on its back side at a radial interval of 120°.
  • the scroll mounting member 5 has its mounting portions 5b mounted on large thickness portions of the fan 3 blades 13c.
  • Three revolving mechanisms 15 are provided on the drive scroll 13 near the edge of the sliding surface 13d with the lap 13a thereon at a circumferential interval of 120°.
  • a driven scroll 14 is provided being connected with above drive scroll, which has a lap 14a engaging with the lap 13a and having lap wall.
  • the lap 14a disposed in sliding surface 14d of the driven scroll 1" is opposite in the involute shape to the lap 13a of the drive scroll 13.
  • the driven scroll 14 has a hole 14e, which is concentric with the axis of its rotation and communicates the sliding surface 14d with the outside for discharging compressed fluid to the outside.
  • the driven scroll 14 has the same dimensions and shape as the drive scroll 13.
  • the driven scroll 14 further has a cylindrical passage-forming portion 14f, which surrounds the opening of the hole 14e and has an end portion fitted in an end portion 10c of a communication bore of a scroll mounting member 10 to be described later.
  • the lap 14a noted above has a tip groove formed in its tip facing the opposed sliding surface, and a tip seal 22 of a self-lubricating material such as a fluorine-based resin is fitted in the tip groove.
  • the drive scroll 13 has a passage 13f like the passage 14f, but this passage 13f is not used because no hole like the hole for discharging compressed fluid to the outside is provided to the outside in the driven scroll.
  • the driven scroll 14 has three fan blades 14c provided on the back side at radial interval of 120°, and mounting portions of the scroll mounting member 10 to be described later are mounted on large thickness portions of the fan blades 14c.
  • Three revolving mechanisms 15 are provided on the driven scroll 14 near the edge of the sliding surface 14d at a circumferential interval of 120°. Via these revolving mechanisms 15, the driven scroll 14 is revolved about an axis of rotation eccentric with the axis of rotation of the drive scroll 13.
  • a dust seal housing 8 is provided between the sliding surfaces 13d and 14d of the drive and driven scrolls 13 and 14 such that it surrounds and forms a predetermined space from the outer wall of laps with the laps of the drive/driven scrolls.
  • the dust seal housing 8 is a doughnut-like die-casting having a predetermined thickness. It forms an outer peripheral wall of the apparatus and has a fluid suction port 8a. It has dust seals 8b and 8c of a self-lubricating material such as a fluorine-based resin. The dust seals 8b and 8c are located at positions corresponding to the neighborhood of the outer periphery of the sliding surfaces 13d and 14d of the drive and driven scrolls 13 and 14.
  • the dust housing surface is in frictional contact with the drive and driven scrolls 13 and 14 being putting dust seal 8b and 8c between both scrolls.
  • the dust seal housing 8 is held at a position (not shown) in the neighborhood of its outer periphery of dust seal housing 8 and at sand-witch-like between the scroll housing 6 and a scroll housing 7 to be described later.
  • the scroll mounting member 10 which is mounted on large thickness portions of the fan blades 14c provided on the back side of the driven scroll 14, is substantially mushroom-like in shape, and has a communication bore extending through its stem portion and flaring portion for discharging compressed fluid to the outside.
  • the driven scroll 14 has a passage-forming portion 14f, which is fitted in an end portion 10c of the communication bore.
  • the driven scroll 14 is secured to the scroll mounting member 10b.
  • the scroll mounting member 10 has three holes 10a, which are formed in the flaring portion other than the mounting portions for passing cooling air.
  • a rotary bearing 17 is fitted on the flaring portion of the scroll mounting portion 10, and its outer periphery is secured to the scroll housing 7.
  • the dust seal housing 8 is held at a position (not shown) near the outer periphery in the form of sand-witch between scroll housing 6 and scroll housing 7.
  • the scroll mounting member 10 is disposed for rotation in the scroll housing 7 in the state with the driven scroll 14 secured to it.
  • the peripheral wall of the scroll housing 7 has a hole 7a, through which air having cooled the driven scroll 14 is released to the outside.
  • a scroll mounting member cover 11 is mounted on the scroll housing 7 such as to cover the flaring portion of the driven scroll mounting member 10.
  • a seal member 16 having a opening hole in the central portion is mounted disposed with the openin" hole on the surrounding of the discharge opening 10d of above mounting member 10.
  • the seal retainer which secured to the seal member 16 is disposed to the scroll mounting member cover 11, through which discharged fluid is prevented from flowing through the outer periphery of discharged exit 10d to the back side of the driven scroll 14.
  • the seal retainer 12 has an opening 12a for discharging compressed fluid.
  • the scroll mounting member cover 11 has a through opening 11a. Air entering from the through hole 11a flows through an opening 10a in the scroll mounting member 10 to the back side of the driven scroll 14, and it can be released by the fan blades 14c through the opening 7a in the scroll housing 7 to the outside.
  • the rotary bearing 17 is held pushed by a bearing retainer 4, which is mounted in a mounting portion 6b of the scroll housing 6 via a spring 19 by bolts 20 such that it is adjustable in thrust directions.
  • Adjusting means is constituted by the bearing retainer 4, bolts 20, etc.
  • rotation of the drive shaft 18 causes fluid to be sucked through the suction port 8a provided in the dust seal housing 8, causing fluid in the space formed by the laps 13a and 14a and the dust seal housing 8 to be taken and progressively compressed by the laps 13a and 14a, and discharged through the discharge port 14e provided in the driven scroll 14.
  • This operation is performed continuously. During this operation, air is caused to flow through the opening 4a in the bearing retainer 4, and fed through the opening 5a in the scroll mounting member 5 and the concave space 13b in the drive scroll 13 to cool the scroll plate. The air having cooled the drive scroll 13 is released through the opening 6a in the scroll housing 6 to the outside with the rotation of the fan blades 13c.
  • the surface 7b of the scroll housing 7 and the stepped portion 7c of the rotary bearing 17 can be formed with considerably high accuracy. High accuracy can be further obtained with respect to the thickness of the mounting portion 10b of the scroll mounting member 10 for mounting the scroll plate and the dimension between the sliding surface 14d of the driven scroll and the scroll mounting portion 10b.
  • the distance between the scrolls thus can be adjusted by causing advancement and retreat the rotary bearing 17 of the driven scroll 13 in the thrust directions with the surface 7b of the scroll housing 7 as a reference and securing the bearing retainer 4 in a suitable position by the bolts 20.
  • the bearing retainer 4 causes flexing of the spring 19 to cause flexing of elastically displaceable means via rotary bearing 17, which is constituted by an elastic member 23, such as a rubber piece, a washer, etc., and causes displacement of the drive scroll 13 to the left via the scroll mounting member 5.
  • rotary bearing 17 which is constituted by an elastic member 23, such as a rubber piece, a washer, etc.
  • the bearing retainer 4 When an excessive pushing force is applied to it, the bearing retainer 4 bears an excessive load at its stopped position, thus reducing the durability and economy. In such a case, the bearing retainer 4 should be returned slightly (for instance by 0.2 to 0.3 mm) after it has been stopped.
  • Fig. 3 shows a different example of the elastically displaceable means.
  • This means is provided between bearing and scroll housing.
  • a stepped portion 6c of the scroll housing 6 in which the rotary bearing 17 is supported has recesses 6d and 6e imparting elasticity to it.
  • the stepped portion 6c is bent as shown by the phantom line, and line 17aA of contact between the rotary bearing 17 and the stepped portion 6c is shifted to the left as shown by the phantom line 17aB.
  • the distance between the scrolls can be adjusted in this way.
  • the drive scroll side bearing 17 to the housing 6 and provide a scroll mounting member cover 11, instead of the bearing retainer 4, for axial adjustment by the bolts 20.
  • the distance between the two scrolls can be adjusted by advancing or retreating the rotary bearing 17 of the driven scroll 14 in the thrust direction with the surface 6d of the scroll housing 6 as a reference and securing the scroll mounting member cover 11 in a suitable position by the bolts 20.
  • Fig. 4 is a sectional view showing an example of shaft seal structure in the scroll fluid apparatus according to the invention.
  • Fig. 5 is an enlarged-scale sectional view showing part C shown in Fig. 4.
  • Air sucked through the suction port 8a is compressed in sealed spaces which are formed by the driven scroll 14 revolved relative to the drive scroll 13 by the revolving mechanisms 15. and above air progressively reduced in volume and discharged through the discharge port 14e provided in the driven scroll 14 at the center thereof.
  • a pin 100e is fitted in the outer periphery of the fitted portion 100c to cause rotation of the sleeve seal 101 in unison with the scroll mounting member 100.
  • a seal plate 102 is secured to the seal retainer 103 having above discharged opening 12a so that it is in rotating and sealing contact with the corresponding cylindrical end of the sleeve seal 101.
  • the seal retainer 103 is bolted to the scroll mounting cover 11.
  • the sleeve seal 101 is made of a synthetic resin which is self-lubricating and capable of withstanding increased temperatures to due heat of compression, for instance those composed of PTFE (polytetrafluoroethylene), PPS (polyethylene sulfide), PEEK (polyether etherketone), etc. and containing fillers for improving the lubricating property and durability, and those based on molybdenum dioxide.
  • PTFE polytetrafluoroethylene
  • PPS polyethylene sulfide
  • PEEK polyether etherketone
  • the cylindrical sleeve seal 101 has at its right end a rectangular notch 100g which "he edge of cylindrical end portion is opened. and a pin 100e fitted in the outer periphery of the scroll mounting member 100 is inserted in the notch 100g.
  • the bore of the sleeve seal 101 has a discharge end portion 101a and a fitted portion 101b, the portion 101b being smaller in diameter than the portion 101a. Discharge fluid pressure is applied to the diameter difference area, thus always providing a force tending to push the sleeve seal 101 to the seal plate 102.
  • the diameter of the discharge ends portion 101a is set to an adequate value to obtain an adequate sliding surface pressure as the pushing force in dependence on a predetermined discharge pressure, etc. of the scroll fluid apparatus.
  • the seal plate 102 is made of a ceramic or steel, with its sliding surface hardened by annealing of steel, hard plating on metal, etc.
  • the sliding surface is hard surface finished and is highly wear-resistant.
  • the seal 102 is secured to the to the seal retainer 103 by pressure fitting, driving or using an adhesive.
  • the seal plate 102 is thus hardly worn out although the sleeve seal 101 is worn out.
  • the seal 102 has a diameter greater than the diameter of the sleeve seal 101 to allow a slight deviation during assembling of the scroll mounting member 100.
  • Fig. 6 is an enlarged-scale sectional view showing a different example of the part C shown in Fig. 4.
  • the scroll mounting member 30 of the driven scroll 14 is fitted in the sleeve seal 31, and the seal plate 32 is secured by Pressure fitting to the driven scroll mounting member 30 for rotation in unison therewith.
  • the seal retainer 33 has an anti-rotation key groove, and the sleeve seal 31 has a raised key convex portion 31e which is redundantly fitted in the key groove for keying in order to stop rotation, and the seal sleeve 31 is inserted slidably in the direction of central axis of the mounting member 30.
  • the pressure of compressed fluid discharged in the scroll fluid apparatus is applied to the area corresponding to the difference between the outer and inner diameters 31b and 31a of the sleeve seal 31 from a gap 31g adjacent the left end of seal sleeve 31 which is contacted to push the polishing surface of seal plate 32.
  • the seal retainer 33 has the O-ring groove 33f, in which the O-ring is fitted to block external air.
  • the sleeve seal 31 is not rotated relative to the seal retainer 33 while being axially alidable, and the sleeve seal plate 32 instead is secured to and rotatable in unison with the scroll mounting member 30.
  • the same functions and effects as described before in connection with Fig. 5 are obtainable.
  • Figs. 7 to 10 show further examples of the part C shown in Fig. 4.
  • the example shown in Fig. 7 seeks to reduce the material of the of the sleeve seal 41.
  • the seal plate is designated at 43.
  • the sleeve seal 41 has a portion held between seal holding members 41h and 41i.
  • the fitted portion 41b of the scroll "ounting member and the and the sleeve seal 41a have different inner diameters, causing the seal 43 to be pushed by fluid pressure.
  • the designated 40e is a pin which is fitted in the mounting member 40, 40b is O-ring groove, 41g and 41j show the rectangular groove hole, for which those function is same as the explanation of Fig. 5.
  • the example shown in Fig. 8 is a system, in which a fitted portion 51b of the sleeve seal 51 is fitted in the driven scroll mounting member 50.
  • the sleeve seal 51 has an O-ring groove 51f, in which the O-ring is fitted.
  • the sleeve seal 51 is pushed against the seal plate 52 by the pressure applied to the area corresponding to the difference between the outer and inner diameters 51b and 51a of the sleeve seal 51.
  • 50g is a rectangular groove hole
  • 50e is a pin which is mounted in the above groove hole 50g and the same functions and effects as described before in connection with Fig. 5 are obtainable.
  • Fig. 9 The example shown in Fig. 9 is the same as the structure shown in Fig. 5 insofar as the anti-rotation pin 60e inserted in the driven scroll mounting member 60, the O-ring groove 60f and the O-ring are concerned.
  • the surface of the seal plate 62 in frictional contact with the sleeve seal 61 has a slight taper with an angle ⁇ . The area of the frictional contact surfaces is thus reduced to let these surfaces more quickly intimate with each other.
  • the example shown in Fig. 5 is the same as the structure shown in Fig. 5 insofar as the anti-rotation pin 70e inserted in the driven scroll mounting member 70, the O-ring groove 70f and the O-ring are concerned.
  • the surface of the sleeve seal 71 in frictional contact with the seal plate 72 has a slight taper with an angle ⁇ . The same functions and effects as in the case of Fig. 5 are obtainable.
  • the sleeve seal 101 has a rectangular notch 100g open at an end, so that it can be readily fitted in an inserted portion 100c of the scroll mounting portion 100.
  • the pushing force with which to have the end surface of the sleeve seal 101 in frictional and sealing contact is determined mainly by the diameter of the discharge side hole 101a of the sleeve seal 101 and the discharge pressure of the scroll fluid apparatus, and the diameter of the discharge side hole 101a is set to an adequate value in dependence on the kind of the apparatus.
  • the following advantages are obtainable. Since nearly a central portion of the drive scroll on the side thereof opposite the lap is supported in the scroll housing via the supporting means, which is position adjustable displaceably in the axial direction of the scroll. Therefore, it would not be necessary to adjust a plurality of adjusting means provided near scroll plate outer periphery. The outer periphery portion of the scroll plate thus would not be in partial contact and driving on squeak contact with the opposed scroll due to excessive displacement of a one of the plural adjusting means. It is thus possible to improve the durability.
  • the central portion of scroll plate is held by supporting means that is supported in the housing, by which the supporting means are displaceable adjusted. Therefore, the supporting means are inclined aslant by the displacement adjustment for the outer peripheral portion of scroll plate and the driving of scroll plate between the supporting means and the housing portion supported the supporting means is not caused any unjustifiable friction. Therefore, durability is improved.
  • the displaceable adjustment of the supporting means supporting the central portion of the scroll allows the position control with respect to a reference surface in a narrow range centered on the supporting means, compared to the case of adjusting a plurality of adjusting means provided near the outer periphery of scroll plate. It is thus possible to reduce the steps of manufacture.
  • the scroll fluid apparatus of rotating drive/driven type comprises the drive and driven scrolls via their supporting means. That is., both the drive and driven scroll plates are rotated about their supporting means.
  • the displacement adjusting member should not be held in the housing over the entire circumference, but the supporting means should be displaceably adjusted at the central portion of scroll plate, therefore the construction is made simply.
  • the dust seal housing which supports the outer peripheral neighborhood of the lap formative face side of each of the scroll plates, defines the distance between the both scroll plates by the above dust seal housing, thus permitting adjustment of the central portions of the scrolls with the supporting means. It is thus possible to easily adjust the distance between the scroll plates.
  • the dust seal housing also positions the outer periphery of the both scroll plates. It is thus possible to prevent deviations of the scroll outer periphery in the axial direction during driving due to fabrication errors or like causes, thus because of eliminating generation of vibrations, the durability is improved.
  • the supporting means are supported in the elastically displaceable means displaceable in the axial direction, they can be secured to the scroll housings by the elastically displaceable means after the scroll plates displaceable adjustment. It is thus possible to prevent some noise generation thereof via vibrations of the supporting means due to vibrations of the scroll plates during driving thereof. It is also possible to prevent the friction via abnormal engagement with the opposite side member between the scrolls due to vibrations thereof, thus durability is improved.
  • the intermediate seal member having the inner compressed fluid passage is disposed between the discharge opening for discharging compressed fluid to the outside of the housing and the discharge exit for discharging compressed fluid of scroll plates; and a one end of the intermediate seal member is in gas-tight contact with the above compressed fluid discharging exit so as to be movable in the extending direction of the above compressed fluid passage; moreover, the other end of the intermediate seal member is disposed being facing with the edge of the discharge opening, and the pressure of the compressed fluid serves to have the other end of the intermediate seal member and the edge of the discharge opening contact in gas-tight with each other.
  • the two contact surfaces of the seal plate and the sleeve seal in contact with each other is formed as curved surface, the two contact surfaces can readily become intimate due to small contact surface size, thus readily forming a gas tight state of seal.
  • the distance and the state of engagement between the two scrolls are adjustable with a simple construction, and the thrust adjustment of scroll is adjustable after the above drive scroll has been assembled in its housing, for which permits rough setting of the machining and assembling accuracies of various parts related to the thrust adjustment. This leads to the reduction of the machining and assembling costs.
  • Simplification of the construction of sleeve seal can be obtained with the shaft seal structure which is preventing from leak to the scroll back side of discharged fluid by the sleeve seal member slidably fitted in the driven scroll mounting member and the seal plate for receiving the sleeve seal member pushed by the pressure of fluid being discharged.
  • a sleeve seal which is stable and durable for long time is thus obtainable.
  • the shaft seal structure also can be easily replaced in assembling and maintenance.
EP97100864A 1997-01-21 1997-01-21 Spiralverdrängungsanlage Withdrawn EP0854289A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP97100864A EP0854289A1 (de) 1997-01-21 1997-01-21 Spiralverdrängungsanlage

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP97100864A EP0854289A1 (de) 1997-01-21 1997-01-21 Spiralverdrängungsanlage

Publications (1)

Publication Number Publication Date
EP0854289A1 true EP0854289A1 (de) 1998-07-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP97100864A Withdrawn EP0854289A1 (de) 1997-01-21 1997-01-21 Spiralverdrängungsanlage

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EP (1) EP0854289A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10031141A1 (de) * 2000-06-27 2002-01-17 Knorr Bremse Systeme Spiralkörper
DE10031142A1 (de) * 2000-06-27 2002-01-17 Knorr Bremse Systeme Spiralverdichter und Verwendung des Spiralverdichters
CN110300853A (zh) * 2017-02-17 2019-10-01 三菱重工业株式会社 双旋转涡旋型压缩机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2536292A (en) * 1948-06-03 1951-01-02 Kollsman Paul Rotary fluid pressure seal
DE2935755A1 (de) * 1979-09-05 1981-03-12 Beda-Oxygentechnik, Armaturen Gmbh & Co Kg, 4030 Ratingen Drehverbindung fuer eine leitung.
WO1993017239A1 (en) * 1992-02-20 1993-09-02 Arthur D. Little, Inc. Windage loss reduction arrangement for scroll fluid device
US5391065A (en) * 1993-10-26 1995-02-21 Ingersoll-Rand Company Parallel adjustment assembly for a scroll compressor
WO1995027143A1 (en) * 1994-04-05 1995-10-12 Puritan-Bennett Corporation Scroll compressor
EP0747598A2 (de) * 1995-06-07 1996-12-11 Copeland Corporation Verdrängungsregelbare Spiralmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2536292A (en) * 1948-06-03 1951-01-02 Kollsman Paul Rotary fluid pressure seal
DE2935755A1 (de) * 1979-09-05 1981-03-12 Beda-Oxygentechnik, Armaturen Gmbh & Co Kg, 4030 Ratingen Drehverbindung fuer eine leitung.
WO1993017239A1 (en) * 1992-02-20 1993-09-02 Arthur D. Little, Inc. Windage loss reduction arrangement for scroll fluid device
US5391065A (en) * 1993-10-26 1995-02-21 Ingersoll-Rand Company Parallel adjustment assembly for a scroll compressor
WO1995027143A1 (en) * 1994-04-05 1995-10-12 Puritan-Bennett Corporation Scroll compressor
EP0747598A2 (de) * 1995-06-07 1996-12-11 Copeland Corporation Verdrängungsregelbare Spiralmaschine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10031141A1 (de) * 2000-06-27 2002-01-17 Knorr Bremse Systeme Spiralkörper
DE10031142A1 (de) * 2000-06-27 2002-01-17 Knorr Bremse Systeme Spiralverdichter und Verwendung des Spiralverdichters
DE10031141B4 (de) * 2000-06-27 2006-06-29 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Spiralkörper
DE10031142B4 (de) * 2000-06-27 2006-09-07 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Spiralverdichter und Verwendung eines Spiralverdichters
CN110300853A (zh) * 2017-02-17 2019-10-01 三菱重工业株式会社 双旋转涡旋型压缩机
CN110300853B (zh) * 2017-02-17 2020-10-27 三菱重工业株式会社 双旋转涡旋型压缩机

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