EP2806166B1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP2806166B1
EP2806166B1 EP14169609.6A EP14169609A EP2806166B1 EP 2806166 B1 EP2806166 B1 EP 2806166B1 EP 14169609 A EP14169609 A EP 14169609A EP 2806166 B1 EP2806166 B1 EP 2806166B1
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EP
European Patent Office
Prior art keywords
orbiting
wrap
scroll
fixed
rotation shaft
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.)
Active
Application number
EP14169609.6A
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English (en)
French (fr)
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EP2806166A3 (de
EP2806166A2 (de
Inventor
Sanghun Seong
Kangwook Lee
Yongkyu Choi
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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Filing date
Publication date
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Publication of EP2806166A2 publication Critical patent/EP2806166A2/de
Publication of EP2806166A3 publication Critical patent/EP2806166A3/de
Application granted granted Critical
Publication of EP2806166B1 publication Critical patent/EP2806166B1/de
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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • 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
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
    • 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
    • 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

Definitions

  • the present disclosure relates to a scroll compressor, and particularly, to a scroll compressor having a structure that a rotation shaft is overlapped with a wrap of an orbiting scroll.
  • a scroll compressor indicates a compressor configured to suck and compress a refrigerant under a structure that an orbiting scroll performs an orbital motion with respect to a fixed scroll, in a state where a fixed wrap of the fixed scroll has been engaged with an orbiting wrap of the orbiting scroll.
  • a compression chamber composed of a suction chamber, an intermediate pressure chamber and a discharge chamber is consecutively moved between the fixed wrap and the orbiting wrap.
  • Such scroll compressor is more advantageous than other types of compressors in the aspect of vibration and noise, since it performs a suction process, a compression process and a discharge process consecutively.
  • Behavior characteristics of the scroll compressor may be determined by a type of the fixed wrap and the orbiting wrap.
  • the fixed wrap and the orbiting wrap may have any shape. However, it is general that the fixed wrap and the orbiting wrap have a form of an involute curve which can be easily processed.
  • the involute curve has a path formed by the end of a string when the string wound on a basic circle having an arbitrary radius is unwound. In case of using such involute curve, a capacity change rate is constant because the thickness of the wrap is constant. For a high compression ratio, the number of turns of the wrap should be increased. However, in this case, the size of the scroll compressor may be also increased.
  • an orbiting wrap is formed at one side surface of a plate formed in a disc shape.
  • a boss portion is formed on a rear surface of the plate where the orbiting wrap has not been formed, thereby being connected to a rotation shaft which drives the orbiting scroll to perform an orbital motion.
  • Such structure is advantageous in that a diameter of the plate can be reduced, because the orbiting wrap is formed on an almost entire area of the plate.
  • a point of application to which a repulsive force of a refrigerant is applied during a compression operation, and a point of application to which a reaction force to attenuate the repulsive force is applied are spaced from each other in a vertical direction. This may cause an unstable behavior of the orbiting scroll during the operation, resulting in severe vibration or noise.
  • the scroll compressor has a structure that a coupling point between a rotation shaft 1 and an orbiting scroll 2 is formed on the same surface as an orbiting wrap 2a.
  • a point of application to which a repulsive force of a refrigerant is applied and a point of application to which a reaction force to attenuate the repulsive force is applied are same, a phenomenon that the orbiting scroll 2 is tilted can be solved.
  • An Oldham ring 4 configured to prevent rotation of the orbiting scroll 2, is installed between the orbiting scroll 2 and a fixed scroll 3.
  • the orbiting scroll 2 and the Oldham ring 4 perform a relative motion with respect to each other in a state where key recesses 2b and keys 4a are coupled to each other.
  • the Oldham ring 4 induces the orbiting scroll 2 to perform an orbital motion.
  • the key recesses 2b of the orbiting scroll 2 and the keys 4a of the Oldham ring 4 are coupled to each other with a tolerance gap ( ⁇ 1) of about 10 ⁇ 30 ⁇ m, so that the orbiting scroll 2 can perform a sliding motion with respect to the Oldham ring 4.
  • the conventional scroll compressor may have the following problems. As shown in FIG. 2 , due to the tolerance gap ( ⁇ 1) between the key recesses 2b of the orbiting scroll 2 and the keys 41 of the Oldham ring 4, a rotation moment occurs when the orbiting scroll 2 performs an orbital motion. Due to such rotation moment, offset is generated at a specific part between the orbiting wrap 2a of the orbiting scroll 2 and the fixed wrap 3a of the fixed scroll, i.e., at both sides of an arc compression surface based on contact points formed by a tangent line and the arc compression surface, the tangent line drawn at a center of a rotation shaft coupling portion of the orbiting scroll 2 toward the arc compression surface.
  • interference (A) occurs between the orbiting wrap 2a and the fixed wrap 3a as shown in FIG. 3 . Due to such interference (A), a leakage gap (B) between the orbiting wrap 2a and the fixed wrap 3a occurs at other parts. This may cause compression loss.
  • EP 2 581 605 (A2) relates to a scroll compressor with a bypass hole capable of preventing an excessive pressure increase within a compression chamber.
  • EP 0 907 024 (A1) relates to the shape of a scroll body for the purpose of enhancing the performance of the compressor and durability of the scroll body.
  • an aspect of the detailed description is to provide scroll compressor capable of preventing occurrence of a leakage gap between an orbiting wrap of an orbiting scroll and a fixed wrap of a fixed scroll, by preventing interference between the orbiting wrap and the fixed wrap.
  • a scroll compressor comprising: a hermetic container; a fixed scroll having a fixed wrap; an orbiting scroll having an orbiting wrap which forms a compression chamber by being engaged with the fixed wrap, having a rotation shaft coupling portion at a center portion thereof, having an arc compression surface which forms the compression chamber around the rotation shaft coupling portion, and performing an orbital motion with respect to the fixed scroll; and a rotation shaft having an eccentric portion which is coupled to the orbiting scroll, the eccentric portion overlapped with the orbiting wrap in a radial direction, wherein an interference prevention portion is formed at the fixed wrap or the orbiting wrap such that an interval between the fixed wrap and the orbiting wrap is larger than an orbiting radius of the orbiting wrap.
  • the interference prevention portion may be formed at the arc compression surface.
  • the interference prevention portion may be formed such that a starting point and an ending point thereof are included in the arc compression surface.
  • the scroll compressor may further include an Oldham ring coupled to the orbiting scroll and configured to prevent rotation of the orbiting scroll.
  • tolerance gap may be formed between the orbiting scroll and the Oldham ring, and a maximum depth of the interference prevention portion may be equal to or smaller than the tolerance gap.
  • a plurality of key recesses may be formed at the orbiting scroll in a radial direction, such that keys of the Oldham ring are coupled thereto.
  • the rotation shaft may be coupled to the rotation shaft coupling portion of the orbiting scroll by passing through the fixed scroll.
  • a scroll compressor including: a fixed scroll having a fixed wrap; an orbiting scroll having an orbiting wrap which forms a first compression chamber and a second compression chamber on an outer side surface and an inner side surface thereof by being engaged with the fixed wrap, having a rotation shaft coupling portion at a center portion thereof, having an arc compression surface which forms the first compression chamber around the rotation shaft coupling portion, and performing an orbital motion with respect to the fixed scroll; and a rotation shaft having an eccentric portion which is coupled to the rotation shaft coupling portion of the orbiting scroll, the eccentric portion overlapped with the orbiting wrap in a radial direction, wherein the arc compression surface is spaced from a side wall surface of the fixed wrap by an orbiting radius, and wherein a distance between the fixed wrap and the orbiting wrap is equal to the orbiting radius at a first curved surface of the arc compression surface from a first point where the arc compression surface starts to an arbitrary second point, the distance is longer than the orbiting radius at a second
  • a curvature of the second curved surface may be larger than that of the first curved surface or the third curved surface.
  • the scroll compressor may further include an Oldham ring coupled to the orbiting scroll and configured to prevent rotation of the orbiting scroll.
  • tolerance gap may be formed between the orbiting scroll and the Oldham ring, and a maximum depth of the second curved surface may be equal to or smaller than the tolerance gap.
  • a plurality of key recesses may be formed at the orbiting scroll in a radial direction, such that keys of the Oldham ring are coupled thereto.
  • the rotation shaft may be coupled to the rotation shaft coupling portion of the orbiting scroll by passing through the fixed scroll.
  • a scroll compressor including: a fixed scroll having a fixed wrap; an orbiting scroll having an orbiting wrap which forms a first compression chamber and a second compression chamber on its outer side surface and inner side surface by being engaged with the fixed wrap, and performing an orbital motion with respect to the fixed scroll; a rotation shaft having an eccentric portion overlapped with the orbiting wrap in a radial direction; and a driving unit configured to drive the rotation shaft, wherein a rotation shaft coupling portion, to which the eccentric portion is coupled, is formed in a central portion of the orbiting scroll, wherein a protruded portion is formed on an inner circumferential surface of an inner end portion of the fixed wrap, wherein a recess portion, which forms a compression chamber by contacting the protruded portion, is formed on an outer circumferential surface of the rotation shaft coupling portion, and wherein an interference prevention portion is formed at the fixed wrap or the orbiting wrap such that an interval between the fixed wrap and the orbiting wrap is larger than an orbiting
  • the interference prevention portion may be formed at the arc compression surface.
  • the interference prevention portion may be formed such that a starting point and an ending point thereof are included in the arc compression surface.
  • the scroll compressor may further include an Oldham ring coupled to the orbiting scroll and configured to prevent rotation of the orbiting scroll.
  • tolerance gap may be formed between the orbiting scroll and the Oldham ring, and a maximum depth of the interference prevention portion may be equal to or smaller than the tolerance gap.
  • a plurality of key recesses may be formed at the orbiting scroll in a radial direction, such that keys of the Oldham ring are coupled thereto.
  • a thickness of the rotation shaft coupling portion may be increased within a predetermined section, toward an opposite direction to a moving direction of the compression chamber at the recess portion.
  • a thickness of the fixed wrap may be decreased within a predetermined section, toward an opposite direction to a moving direction of the compression chamber at the protruded portion.
  • the interference prevention portion may be formed on a side wall surface of at least one of a fixed wrap and an orbiting wrap.
  • the end of the fixed wrap does not interfere with the orbiting wrap at an arc compression surface of the orbiting wrap, but is inserted into the interference prevention portion. Accordingly, occurrence of a gap between the fixed wrap and the orbiting wrap can be prevented, and thus compression efficiency can be enhanced.
  • a driving motor 20 may be installed in a hermetic container 10, and a fixed scroll 30 integrally formed with a main frame may be fixedly installed above the driving motor 20.
  • An orbiting scroll 40 which is engaged with the fixed scroll 30 and configured to compress a refrigerant while performing an orbit motion by being coupled to a rotation shaft 23 of the driving motor 20, may be installed above the fixed scroll 30.
  • the hermetic container 10 may include a cylindrical casing 11, and an upper shell 12 and a lower shell 13 coupled to an upper part and a lower part of the casing 11 by welding so as to cover the upper part and the lower part of the casing 11.
  • a suction pipe 14 may be installed on a side surface of the casing 10, and a discharge pipe 15 may be installed above the upper shell 12.
  • the lower shell 13 may also serve as an oil chamber for storing therein oil to be supplied to the compressor for a smooth operation of the compressor.
  • the driving motor 20 may include a stator fixed to an inner surface of the casing 10, and a rotor 22 positioned in the stator 22 and rotating by a reciprocal operation with the stator 22.
  • a rotation shaft 23, which rotates together with the rotor 22, may be coupled to a central part of the rotor 22.
  • An oil passage (F) may be penetratingly-formed at a central region of the rotation shaft 23, in a lengthwise direction.
  • An oil pump 24, configured to supply oil stored in the lower shell 13 to the upper side, may be installed at a lower end of the rotation shaft 23.
  • a pin portion 23c may be formed at an upper end of the rotation shaft 23, in an eccentric manner from the center of the rotation shaft.
  • the fixed scroll 30 may be fixed as its outer circumferential surface is forcibly-inserted between the casing 11 and the upper shell 12 by shrinkage fitting.
  • the fixed scroll 30 may be coupled to the casing 11 and the upper shell 12 by welding.
  • a boss portion 32 may be formed at a central region of a plate portion 31 of the fixed scroll 30.
  • a shaft accommodating hole 33 configured to accommodate the rotation shaft 23 in a penetrating manner, may be formed at the boss portion 32.
  • a fixed wrap 34 may be formed on an upper surface of the plate portion 31 of the fixed scroll. The fixed wrap 34 is engaged with an orbiting wrap to be explained later, and forms a first compression chamber (S1) on an outer side surface of the orbiting wrap 42 and a second compression chamber (S2) on an inner side surface of the orbiting wrap 42.
  • the orbiting scroll 40 may be supported at an upper surface of the fixed scroll 30.
  • the orbiting scroll 40 may include the plate portion 41 formed in an approximately circle shape, and the orbiting wrap 42 formed on an upper surface of the plate portion 41.
  • the orbiting wrap 42 forms a pair of compression chambers S1 and S2 which move consecutively, by being engaged with the fixed wrap 34.
  • Each of the compression chambers S1 and S2 may be composed of a suction chamber, an intermediate pressure chamber and a discharge chamber.
  • a rotation shaft coupling portion 43 which has an approximately circle shape and to which the pin portion 23c of the rotation shaft 23 is rotatably insertion-coupled, may be formed at a central region of the plate portion 41.
  • the pin portion 23c of the rotation shaft 23 may be insertion-coupled to the rotation shaft coupling portion 43.
  • the pin portion 23c may be coupled to the rotation shaft coupling portion 43 of the orbiting scroll 30, through the plate portion 31 of the fixed scroll 30.
  • the orbiting wrap 42, the fixed wrap 34 and the pin portion 23c may be formed to overlap one another, in a radius direction of the scroll compressor.
  • a repulsive force of a refrigerant is applied to the fixed wrap 34 and the orbiting wrap 42.
  • a compressive force is applied between the rotation shaft coupling portion 43 and the pin portion 23c.
  • a repulsive force of a refrigerant and a compressive force are applied to the same side surface based on the plate portion 41 of the orbiting scroll. Therefore, the repulsive force and the compressive force may be attenuated from each other.
  • An Oldham ring 50 configured to prevent rotation of the orbiting scroll 40, may be coupled to an upper side of the orbiting scroll 40.
  • the Oldham ring 50 may include a ring portion 51 having an approximately circle shape and fitted into a rear surface of the plate portion 41 of the orbiting scroll 40, and a pair of first keys 52 and a pair of second keys 53 protruding from one side surface of the ring portion 51.
  • the first keys 52 may be protruded with a length greater than a thickness of an outer circumferential surface of the plate portion 41 of the orbiting scroll 40, and may be inserted into first key recesses 31 a of the fixed scroll 30.
  • the second keys 53 may be fitted into second key recesses 41 a formed on an outer circumference of the plate portion 41 of the orbiting scroll 40.
  • the first key recess 31 a and the first key 52 are preferably formed so that both side surfaces of the first key 52 slidably-contact both side surfaces of the first key recess 31 a.
  • the second key recess 41 a and the second key 53 are preferably formed so that both side surfaces of the second key 53 slidably-contact both side surfaces of the second key recess 41 a.
  • the keys 52, 53 contact the key recesses 31 a, 41 a too closely, frictional resistance is increased between the keys 52, 53 and the key recess 31 a, 41 a.
  • the orbiting scroll 40 may not smoothly perform an orbital motion. In order to solve such problem, as shown in FIG.
  • a tolerance gap ( ⁇ 1) may be formed between the key recess 31a and the key 52, and between the key recess 41 a and the key 53.
  • the tolerance gap ( ⁇ 1) is large enough for the orbiting scroll 40 can perform an orbital motion as the keys 52, 53 are smoothly slid on the key recesses 31a, 41 a.
  • Each of the fixed wrap 34 and the orbiting wrap 42 may be formed in an involute curve. However, in some cases, the fixed wrap 34 and the orbiting wrap 42 may be formed in other curve rather than an involute curve.
  • an angle ( ⁇ ) defined by two straight lines is smaller than 360°, the straight lines formed by connecting the center 'O' of the rotation shaft coupling portion 43 to the two contact points 'P1' and 'P2', respectively.
  • a distance (t) between a normal vector of the contact point 'P1' and a normal vector of the contact point 'P2 is larger than 0.
  • the scroll compressor can have an increased compression ratio, because it has a smaller volume than in a case where the first compression chamber (S1) prior to discharge has the fixed wrap 34 and the orbiting wrap 42 of an involute curve.
  • the orbiting wrap 42 and the fixed wrap 34 have a shape that a plurality of arcs having different diameters and origins are connected.
  • the outermost curve may have an approximately oval shape with a major axis and a minor axis.
  • a protruded portion 35 which protrudes toward the rotation shaft coupling portion 43, may be formed near an inner end portion of the fixed wrap 34.
  • a contact portion 35a may be further formed at the protruded portion 35, in a protruding manner from the protruding portion 35. Accordingly, the inner end portion of the fixed wrap may have a larger thickness than other parts.
  • the thickness of the fixed wrap 34 is gradually decreased, starting from the inner contact point P1 of the two contact points (P1, P2) defining the first compression chamber (S1) upon initiating the discharge operation. More specifically, a first decrease part 35b is formed adjacent to the contact point (P1) and a second decrease part 35c is connected to the first decrease part 31 b. A thickness reduction rate at the first decrease part is higher than that at the second decrease part. After the second decrease part, the fixed wrap may be increased in thickness within a predetermined interval.
  • a recess portion 44 which is engaged with the protruded portion 35, may be formed at the rotation shaft coupling portion 43.
  • One side wall of the recess portion 44 may contact the contact portion 35a of the protruded portion 35, thereby forming the contact point 'P1' of the first compression chamber (S1).
  • One side wall of the recess portion 44 may include a first increase part 45a where a thickness is relatively greatly increased, and a second increase part 45b connected to the first increase part 45a and having a thickness increased at a relatively low rate. These correspond to the first decrease part 35b and the second decrease part 35c of the fixed wrap 34.
  • the first increase part 45a, the first decrease part 35b, the second increase part 45b and the second decrease part 35c may be obtained by turning a generating curve toward the rotation shaft coupling portion. Accordingly, the inner contact point (P1) of the first compression chamber (S1) may be positioned at the first increase part and the second increase part, and the length of the first compression chamber right before a discharge operation may be shortened so as to enhance a compression ratio.
  • Another side wall of the recess portion 44 may be formed to have an arc compression surface 46 having a circular shape and formed by connecting lines to one another, the lines formed as the orbiting wrap contacts the end of the fixed wrap 34 while the orbiting scroll 40 performs an orbital motion.
  • a diameter of the arc of the arc compression surface 46 is determined by the wrap thickness of the end of the fixed wrap, and an orbiting radius of the orbiting wrap. If the wrap thickness of the end of the fixed wrap is increased, the diameter of the arc is increased. As a result, the thickness of the orbiting wrap near the arc is increased, and thus durability of the scroll compressor is enhanced. Further, a compression path is increased, and thus a compression ratio of the second compression chamber (S2) is increased.
  • An operation of the scroll compressor according to the present invention is as follows. Once the rotation shaft 43 rotates as power is supplied to the driving motor 40, the orbiting scroll 60 eccentrically-coupled to the rotation shaft 43 performs an orbital motion along a predetermined path. And the compression chamber (P) formed between the orbiting scroll 60 and the fixed scroll 30 moves to the center of the orbital motion consecutively, to thus have a decreased volume. In the compression chamber (P), a refrigerant is sucked, compressed and discharged consecutively. Such processes are repeatedly performed.
  • the orbiting scroll 40 performs an orbital motion while its rotation is prevented by the Oldham ring 50.
  • a tolerance gap ( ⁇ 1) of approximately 10 ⁇ 30 ⁇ m is required between the key recess 41 a of the orbiting scroll 40 and the key 52, and between the key recess 31 a of the fixed scroll 30 and the key 53, so that the orbiting scroll 40 and the Oldham ring 50 can perform a sliding motion with respect to each other.
  • the orbiting scroll 40 generates a rotation moment due to the tolerance gap ( ⁇ 1).
  • wrap interference (A) may occur between the fixed wrap 34 and the orbiting wrap 42 as shown in FIG. 3 .
  • an interference prevention portion 46a having a predetermined depth in a thickness direction of the orbiting wrap 42 may be formed at the arc compression surface 46 of the recess portion 44 of the orbiting scroll 40.
  • the interference prevention portion 46a may be formed to have a depth ⁇ 2 from an orbiting radius (r) which is obtained in a state where the fixed wrap 34 and the orbiting wrap 42 have been aligned to be concentric with each other.
  • a starting point of a second curved surface (P12 ⁇ P13) which forms the interference prevention portion 46a may be positioned at a first curved surface (P11 ⁇ P12) between a first point (P11) where arc compression starts and an arbitrary second point (P12).
  • an ending point of the second curved surface (P12 ⁇ P13) which forms the interference prevention portion 46a may be positioned at a third curved surface (P13 ⁇ P14) between an arbitrary third point (P13) closer to a discharge opening than the second point (P12) and a fourth point (P14) where compression is ended.
  • a depth of the interference prevention portion 46a may be equal to or smaller than tolerance gap ( ⁇ 1). If the depth of the interference prevention portion 46a is larger than the tolerance gap ( ⁇ 1), a gap is generated between the fixed wrap 34 and the orbiting wrap 42. This may cause compression performance to be significantly lowered.
  • an rotation angle (radian) of the rotation shaft 23 is ⁇
  • tolerance gap is ⁇ 1
  • a shortest distance between the second key recess and a center of the rotation shaft coupling portion is L1
  • a shortest distance between a center line of the orbiting wraps and the center of the rotation shaft coupling portion is L2
  • a depth (offset amount) of the interference prevention portion is ⁇ 2.
  • ⁇ 2 may be calculated as follows.
  • the tolerance gap ( ⁇ 1) is 30 ⁇ m
  • the shortest distance (L1) between the second key recess 41 a and a center of the rotation shaft coupling portion 43 is 53 mm
  • the end of the fixed wrap 34 does not interference with the orbiting wrap 42 at the arc compression surface 46 of the orbiting wrap 42, but is inserted into the interference prevention portion 46a. Accordingly, occurrence of a gap between the fixed wrap 34 and the orbiting wrap 42 can be prevented, and thus compression efficiency can be enhanced.
  • the interference prevention portion 46a is formed at the arc compression surface 46 of the orbiting scroll 42.
  • the interference prevention portion 46a may be formed at a starting end of the fixed wrap 34 of the fixed scroll 30, the fixed wrap which corresponds to the arc compression surface 46 of the orbiting scroll 40.
  • an interference prevention portion 32a may be formed to have a predetermined depth in a thickness direction of the fixed wrap 34, on an outer circumferential surface of the fixed wrap 34 which contacts the arc compression surface 46, within a section where arc compression is performed based on the orbiting scroll 40.
  • the depth of the interference prevention portion 32a is equal to or smaller than the tolerance gap ( ⁇ 1) formed between the key recess 41 a of the orbiting scroll 40 and the key 53 of the Oldham ring 50.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (5)

  1. Spiralkompressor, der aufweist:
    einen hermetischen Behälter (10);
    eine feste Spirale (30), die fest mit dem hermetischen Behälter (10) gekoppelt ist und eine feste Hülle (34) hat;
    eine umlaufende Spirale (40) mit einer umlaufenden Hülle (42), die eine Kompressionskammer (P) bildet, indem sie mit der festen Hülle (34) in Eingriff gebracht wird, die einen Drehwellenkopplungsabschnitt (43) in ihrem Mittelabschnitt hat, eine Bogenkompressionsoberfläche (46) hat, die die Kompressionskammer (P) um den Drehwellenkopplungsabschnitt (43) herum hat und aufgebaut ist, um eine Umlaufbewegung in Bezug auf die feste Spirale (30) durchzuführen; und
    eine Drehwelle (23), die einen exzentrischen Abschnitt hat, der mit der umlaufenden Spirale (40) gekoppelt ist, indem sie durch die feste Spirale (30) geht, wobei der exzentrische Abschnitt die umlaufende Hülle (42) in einer Radialrichtung überlappt, und
    einen Oldham-Ring (50), der mit der umlaufenden Spirale (40) gekoppelt ist und aufgebaut ist, um die Drehung der umlaufenden Spirale (40) zu verhindern,
    dadurch gekennzeichnet, dass die feste Spirale (34) oder die umlaufende Spirale (42) einen Störungsschutzabschnitt (46a) aufweist, der an der festen Hülle (34) oder der umlaufenden Hülle (42) ausgebildet ist, so dass ein Abstand zwischen der festen Hülle (34) und der umlaufenden Hülle (42) größer als ein Umlaufradius (r) der umlaufenden Hülle (42) ist, um die Störung zwischen der festen Hülle (34) und der umlaufenden Hülle (42) zu vermeiden, die aufgrund einer Drehbewegung verursacht wird, wobei die Drehbewegung der umlaufenden Spirale (42) sich aus einem Toleranzabstand zwischen der umlaufenden Hülle (42) und dem Oldham-Ring (50) ergibt, wobei der Störungsschutzabschnitt (46a) derart ausgebildet ist, dass sein Anfangspunkt und sein Endpunkt auf der Basis eines Kontaktpunkts zwischen einer Tangentenlinie und der Bogenkompressionsoberfläche (46), wenn die Tangentenlinie von einer Mitte des Drehwellenkopplungsabschnitts (43) in Richtung der Bogenkompressionsoberfläche (46) gezogen wird, in der Bogenkompressionsoberfläche (46) enthalten sind, und wobei die Bogenkompressionsoberfläche (46) von einer Seitenwandoberfläche der festen Hülle (34) um einem Umlaufradius beabstandet ist, wobei ein Abstand zwischen der festen Hülle (34) und der umlaufenden Hülle (42) gleich dem Umlaufradius einer ersten gekrümmten Oberfläche (P11-P12) der Bogenkompressionsoberfläche (46) von einem ersten Punkt (P11), an dem die Bogenkompressionsoberfläche (46) zu einem beliebigen zweiten Punkt (P12) startet, ist,
    wobei der Abstand zwischen der festen Hülle (34) und der umlaufenden Hülle (42) an einer zweiten gekrümmten Oberfläche (P12 - P13) der Bogenkompressionsoberfläche (46) von dem zweiten Punkt (P12) zu einem dritten Punkt (P13), wo eine Bogenkompression durchgeführt wird, länger als der Umlaufradius ist, wobei der Störungsschutzabschnitt (46a) an der zweiten gekrümmten Oberfläche (P12 - P13) ausgebildet ist, und
    wobei der Abstand zwischen der festen Hülle (34) und der umlaufenden Hülle (42) an einer dritten gekrümmten Oberfläche (P13 - P14) der Bogenkompressionsoberfläche von dem dritten Punkt (P13) zu einem vierten Punkt (P14), wo die Bogenkompression beendet wird, gleich dem Umlaufradius ist, und wobei eine Krümmung der zweiten gekrümmten Oberfläche (P12 - P13) größer als die der ersten gekrümmten Oberfläche (P11 - P12) oder der dritten gekrümmten Oberfläche (P13 - P14) ist.
  2. Spiralkompressor nach Anspruch 1, der ferner einen Oldham-Ring (50) aufweist, der mit der umlaufenden Spirale (40) gekoppelt ist und aufgebaut ist, um die Drehung der umlaufenden Spirale (40) zu verhindern, und
    wobei ein Toleranzabstand (δ1) zwischen der umlaufenden Spirale (40) und dem Oldham-Ring (50) ausgebildet ist, und
    wobei eine maximale Tiefe (δ2) des Störungsschutzabschnitts (46a) kleiner oder gleich dem Toleranzabstand (δ1) ist.
  3. Kompressor nach Anspruch 2, wobei mehrere Keilvertiefungen (41a) an der umlaufenden Spirale (40) in einer Radialrichtung ausgebildet sind, so dass Keile (53) des Oldham-Rings (50) damit gekoppelt werden, und
    wobei (δ1×(L2/L1)) - 5 µm ≤ δ2 ≤ (δ1×(L2/L1)) + 5 µm, wobei L1 ein kürzester Abstand zwischen der Keilvertiefung (41a) und einer Mitte des Drehwellenkopplungsabschnitts (43) ist, L2 ein kürzester Abstand zwischen einer Mittellinie der umlaufenden Hüllen (42) und der Mitte des Drehwellenkopplungsabschnitts (43) ist, δ1 ein Toleranzabstand zwischen dem Oldham-Ring (50) und der Keilvertiefung (41a) ist, δ2 eine Tiefe (Versatzgröße) der zweiten gekrümmten Oberfläche ist.
  4. Spiralkompressor nach einem der Ansprüche 1 bis 3, wobei ein vorstehender Abschnitt (35) auf einer Innenumfangsoberfläche eines inneren Endabschnitts der festen Hülle (34) ausgebildet ist,
    wobei ein vertiefter Abschnitt (44), der durch Berühren des vorstehenden Abschnitts (35) eine Kompressionskammer bildet, auf einer Außenumfangsoberfläche des Drehwellenkopplungsabschnitts (43) ausgebildet ist, und
    wobei eine Dicke des Drehwellenkopplungsabschnitts (43) innerhalb eines vorgegebenen Abschnitts an dem vertieften Abschnitt (44) in eine zu einer Bewegungsrichtung der Kompressionskammer (P) entgegengesetzte Richtung vergrößert ist, und
    wobei eine Dicke der festen Hülle (34) innerhalb eines vorgegebenen Abschnitts an dem vorstehenden Abschnitt (35) in Richtung einer zu einer Bewegungsrichtung der Kompressionskammer (P) entgegengesetzten Richtung verringert ist.
  5. Spiralkompressor nach einem der Ansprüche 1 bis 4, wobei die Drehwelle (23) durch die feste Spirale (30) mit dem Drehwellenkopplungsabschnitt (43) der umlaufenden Spirale (40) gekoppelt ist.
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CN113513472B (zh) * 2020-04-10 2024-08-16 谷轮环境科技（苏州）有限公司 涡旋压缩机的静涡旋、用于制造静涡旋的中间件及方法

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JP3495216B2 (ja) * 1997-01-28 2004-02-09 株式会社日立製作所 スクロール圧縮機
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US6527526B2 (en) 2000-12-07 2003-03-04 Lg Electronics, Inc. Scroll compressor having wraps of varying thickness
US7128540B2 (en) * 2001-09-27 2006-10-31 Sanyo Electric Co., Ltd. Refrigeration system having a rotary compressor
CN1847657A (zh) * 2005-10-21 2006-10-18 兰州理工大学 用于燃料电池的无油润滑涡旋压缩机
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