WO2022113559A1 - スクロール圧縮機 - Google Patents

スクロール圧縮機 Download PDF

Info

Publication number
WO2022113559A1
WO2022113559A1 PCT/JP2021/038215 JP2021038215W WO2022113559A1 WO 2022113559 A1 WO2022113559 A1 WO 2022113559A1 JP 2021038215 W JP2021038215 W JP 2021038215W WO 2022113559 A1 WO2022113559 A1 WO 2022113559A1
Authority
WO
WIPO (PCT)
Prior art keywords
movable
wrap
compression chamber
fixed
scroll
Prior art date
Application number
PCT/JP2021/038215
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
淳夫 手島
泰造 佐藤
Original Assignee
サンデン・オートモーティブコンポーネント株式会社
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 サンデン・オートモーティブコンポーネント株式会社 filed Critical サンデン・オートモーティブコンポーネント株式会社
Priority to US18/251,994 priority Critical patent/US20240011488A1/en
Priority to CN202180076524.7A priority patent/CN116457577A/zh
Priority to DE112021004781.7T priority patent/DE112021004781T5/de
Publication of WO2022113559A1 publication Critical patent/WO2022113559A1/ja

Links

Images

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
    • 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
    • F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling movement
    • 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
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement

Definitions

  • the present invention relates to a scroll compressor.
  • the scroll compressor disclosed in Patent Document 1 has a fixed scroll and a movable scroll in which a spiral wrap is erected on the bottom plate and the center of the bottom plate and the center of the base circle of the wrap (the center of the spiral) are eccentric to each other. It is equipped with a scroll unit that forms a closed space by engaging the laps facing each other and a rotation prevention mechanism that prevents the rotation of the movable scroll, and the rotation prevention mechanism prevents the rotation of the movable scroll while the movable scroll. Is revolving around the axis of the fixed scroll to change the volume of the enclosed space.
  • the rotation prevention mechanism is composed of a circular hole formed on the back surface of the bottom plate of the movable scroll and a pin projecting from the housing wall facing the back surface of the bottom plate of the movable scroll and engaging with the circular hole. It is disclosed that it will be done. Further, Patent Document 1 discloses that a rotation moment is generated in a movable scroll due to a compression reaction force accompanying compression by a scroll compressor, and a load due to this rotation moment acts on a rotation prevention mechanism.
  • an object of the present invention is to suppress a decrease in the rotation moment generated in the movable scroll.
  • the scroll compressor includes a fixed bottom plate having a discharge hole in the center, a fixed scroll having a spiral fixed wrap erected on the fixed bottom plate, and a movable bottom plate.
  • a movable scroll having a spiral movable lap that is erected on a movable bottom plate and meshes with the fixed lap, a first compression chamber formed by an inner wall surface of the movable lap and an outer wall surface of the fixed lap, and a fixed wrap.
  • It is equipped with a second compression chamber formed by the inner wall surface and the outer wall surface of the movable lap, and a rotation prevention mechanism that prevents the rotation of the movable scroll, and the rotation prevention mechanism prevents the rotation of the movable scroll while allowing the movable scroll to move.
  • the extension angle from the reference point on the base circle of the fixed wrap to the winding end end of the fixed wrap is the winding end end of the movable wrap from the reference point on the base circle of the movable wrap. Less than the extension angle up to.
  • the second compression chamber is sealed by abutting against the wall surface.
  • the pressure in the first compression chamber is always higher than the pressure in the second compression chamber, so that a rotation moment can always be generated in the movable scroll, and thus a rotation moment can be generated. , It is possible to suppress a decrease in the rotation moment.
  • Sectional drawing of the scroll compressor in one Embodiment of this invention Floor plan of fixed scroll Floor plan of movable scroll AA sectional view of FIG. 3 Enlarged cross-sectional view of the rotation prevention part that constitutes the rotation prevention mechanism Layout of the rotation prevention part of the rotation prevention mechanism on the movable bottom plate
  • the figure which shows the operation state of a scroll compressor The figure which shows the operation state of a scroll compressor
  • the figure which shows the operation state of a scroll compressor The figure which shows the operation state of a scroll compressor
  • the figure which shows the operation state of a scroll compressor The figure which shows the operation state of a scroll compressor
  • the figure which shows the operation state of a scroll compressor The figure which shows the relationship between the pressure in a compression chamber and a crank angle.
  • FIG. 1 is a cross-sectional view showing the overall configuration of the scroll compressor.
  • FIG. 2 is a plan view of a fixed scroll.
  • FIG. 3 is a plan view of the movable scroll.
  • FIG. 4 is a sectional view taken along the line AA of FIG.
  • FIG. 5 is an enlarged cross-sectional view of a rotation prevention portion constituting the rotation prevention mechanism.
  • FIG. 6 is a layout drawing of a rotation prevention portion of the rotation prevention mechanism in the movable bottom plate.
  • the scroll compressor 1 includes a scroll unit 4 having a fixed scroll 2 and a movable scroll (swivel scroll) 3 arranged to face each other in the central axis direction.
  • a scroll unit 4 having a fixed scroll 2 and a movable scroll (swivel scroll) 3 arranged to face each other in the central axis direction.
  • a spiral fixed wrap 2b is integrally erected on the fixed bottom plate 2a.
  • a spiral movable lap (swivel wrap) 3b is integrally erected on the movable bottom plate (swivel bottom plate) 3a.
  • the fixed lap 2b and the movable lap 3b are formed along an involute curve (virtual line) extending from the base circles (virtual circles) 2c and 3c.
  • the extension angle ⁇ 1 shown in FIG. 2 is an angle around the center (fixed spiral center) 2d of the base circle 2c, and is a fixed lap from the reference point (start point of the involute curve) 2e on the base circle 2c. It is an angle up to the winding end end end 2f of 2b.
  • the extension angle ⁇ 1 is smaller than the extension angle ⁇ 2.
  • the extension angle ⁇ 1 is 820 ° and the extension angle ⁇ 2 is 850 °, but the extension angles ⁇ 1 and ⁇ 2 are not limited to these values.
  • the fixed wrap 2b is formed by eccentricizing the center 2d of the base circle 2c with respect to the center (not shown) of the fixed bottom plate 2a.
  • the movable lap 3b is formed by eccentricizing the center 3d of the base circle 3c with respect to the center (not shown) of the movable bottom plate 3a.
  • the fixed scroll 2 and the movable scroll 3 mesh with the fixed lap 2b and the movable lap 3b, the end edge of the fixed lap 2b on the protruding side comes into contact with the movable bottom plate 3a, and the end edge of the movable lap 3b on the protruding side is fixed. It is arranged so as to be in contact with the bottom plate 2a. Tip seals are provided on the protruding end edge of the fixed wrap 2b and the protruding end edge of the movable wrap 3b, respectively.
  • the wall surface of the fixed lap 2b and the wall surface of the movable lap 3b are partially in contact with each other in a state where the angles in the circumferential direction of the fixed lap 2b and the movable lap 3b are different from each other. Arranged to do so. Therefore, in the present embodiment, the crescent-shaped first compression chamber C1 is formed by the inner wall surface 3b1 of the movable lap 3b and the outer wall surface 2b2 of the fixed wrap 2b, and the inner wall surface 2b1 of the fixed wrap 2b and the outside of the movable wrap 3b are formed. A crescent-shaped second compression chamber C2 is formed by the wall surface 3b2 (see FIGS. 7 and 8 described later).
  • the movable scroll 3 is assembled so that the center (axis center) of the movable bottom plate 3a is eccentric with respect to the center (axis center) of the fixed bottom plate 2a. It revolves around the center of 2a.
  • the turning radius of this revolution turning motion may be defined by the contact between the fixed lap 2b and the movable lap 3b. Due to this revolution turning motion, the first compression chamber C1 and the second compression chamber C2 are moved from the winding end end 3f of the movable lap 3b and the winding end end 2f of the fixed lap 2b toward the center portion.
  • the volume of the 1 compression chamber C1 and the volume of the second compression chamber C2 change in the contraction direction, respectively.
  • the fluid (for example, refrigerant gas) taken into the first compression chamber C1 from the winding end end 3f side of the movable lap 3b is compressed, and the second compression chamber is compressed from the winding end end 2f side of the fixed lap 2b.
  • the fluid (for example, refrigerant gas) taken into C2 is compressed.
  • a recess 3h is formed at the winding start end 3g of the movable wrap 3b.
  • the recess 3h is recessed with respect to the inner wall surface 3b1 of the winding start end 3g of the movable wrap 3b.
  • the housing of the scroll compressor 1 is composed of a center housing 6 including a scroll unit 4, a front housing 7 arranged on the front side thereof, and a rear housing 8 arranged on the rear side thereof. ing.
  • the center housing 6 is integrally formed with the fixed scroll 2 as a housing portion (outer shell shell) of the scroll unit 4.
  • the fixed scroll 2 and the center housing 6 may be used as separate members, and the fixed scroll 2 may be stored and fixed in the center housing 6.
  • the rear side of the center housing 6 is closed by the fixed bottom plate 2a, and the front side is open.
  • the front housing 7 is fastened to the opening side of the center housing 6 with bolts (not shown).
  • the front housing 7 supports the movable scroll 3 in the thrust direction and houses the drive mechanism of the movable scroll 3.
  • the front housing 7 is also formed with a suction chamber 9 for the fluid connected to a suction port (not shown) formed on the outer wall of the front housing 7.
  • the front housing 7 and the center housing 6 are formed with a bulging portion 10 in a part in the circumferential direction. Inside the bulging portion 10, the winding end portion 2f of the fixed wrap 2b of the scroll unit 4 on the center housing 6 side from the suction chamber 9 on the front housing 7 side extends in a direction parallel to the center axis of the compressor.
  • a fluid passage space 11 for guiding the fluid is formed in the vicinity and in the vicinity of the winding end end 3f of the movable lap 3b.
  • the rear housing 8 is fastened to the fixed bottom plate 2a side of the center housing 6 with bolts 12 to form the fluid discharge chamber 13 between the rear housing 8 and the back surface of the fixed bottom plate 2a.
  • a discharge hole 14 for the compressed fluid is formed in the central portion of the fixed bottom plate 2a, and the discharge hole 14 is provided with, for example, a discharge valve 15 which is a one-way valve.
  • the discharge hole 14 is connected to the discharge chamber 13 via the discharge valve 15.
  • the discharge chamber 13 is connected to a discharge port (not shown) formed on the outer wall of the rear housing 8.
  • the fluid is introduced from the suction port into the suction chamber 9 in the front housing 7, passes through the fluid passage space 11 inside the bulging portion 10 of the front housing 7 and the center housing 6, and is the first from the outer peripheral side of the scroll unit 4. It is taken into the first compression chamber C1 and the second compression chamber C2 and subjected to compression.
  • the fluid compressed in the first compression chamber C1 and the fluid compressed in the second compression chamber C2 are put together in the rear housing 8 from the discharge hole 14 formed in the central portion of the fixed bottom plate 2a. Is discharged to the discharge chamber 13 of the above, and is led out from there to the outside via the discharge port.
  • the front housing 7 faces the back surface of the movable bottom plate 3a and applies the thrust force from the movable scroll 3 to the inside of the outer peripheral portion fastened to the opening side of the center housing 6 by bolts (not shown) via the thrust plate 16. It has a thrust receiving portion 17 to receive.
  • the front housing 7 also rotatably supports a drive shaft 20 that forms the core of the drive mechanism of the movable scroll 3 in the center.
  • One end side of the drive shaft 20 projects to the outside of the front housing 7, and the pulley 22 is attached to the outside of the front housing 7 via an electromagnetic clutch 21. Therefore, the drive shaft 20 is rotationally driven by the rotational driving force input from the pulley 22 via the electromagnetic clutch 21.
  • the other end side of the drive shaft 20 is connected to the movable scroll 3 via a crank mechanism.
  • the crank mechanism comprises a cylindrical boss portion 23 protruding from the back surface of the movable bottom plate 3a, and an eccentric bush 25 attached to the crank 24 provided at the end of the drive shaft 20 in an eccentric state.
  • the eccentric bush 25 is fitted inside the boss portion 23 via a bearing (for example, a slide bearing) 26.
  • a balancer weight 27 facing the centrifugal force during operation of the movable scroll 3 is attached to the eccentric bush 25.
  • the rotation prevention mechanism 30 includes a ring 31 press-fitted into a circular hole formed in the back surface of the movable bottom plate 3a (facing the thrust receiving portion 17 of the front housing 7) and a thrust receiving portion of the front housing 7.
  • the rotation prevention portion 33 including the pin 32 protruding from the portion 17 side and penetrating the thrust plate 16 and loosely fitted inside the ring 31 is outside the back surface of the movable bottom plate 3a. It is configured by arranging a plurality of (five in this embodiment) at equal intervals along the circumferential direction in the vicinity of the peripheral edge. If there are at least three rotation prevention portions 33, the movable scroll 3 can revolve around the axis of the fixed scroll 2 without rotating.
  • FIGS. 7 to 13 show the operating state of the scroll compressor 1.
  • FIG. 12 is a diagram showing the relationship between the pressure in the first compression chamber C1, the pressure in the second compression chamber C2, and the pressure in the final compression chamber C4, and the crank angle.
  • FIG. 13 is a diagram showing the relationship between the force acting on the pin 32 (rotational moment) and the crank angle.
  • the solid line curve shown in FIG. 13 corresponds to the scroll compressor 1 of the present embodiment
  • the broken line curve shown in FIG. 13 corresponds to the conventional scroll compressor.
  • the above-mentioned extension angle ⁇ 1 and extension angle ⁇ 2 are the same, and the size of the recess 3h (at least the length in the direction along the involute curve of the movable lap 3b). However, it is smaller than that of the present embodiment.
  • the drive shaft 20 When the pulley 22 is rotated by a rotational driving force from the outside, the drive shaft 20 is rotated via the electromagnetic clutch 21, and the movable scroll 3 is prevented from rotating by the rotation prevention mechanism 30 while the fixed scroll 2 is prevented from rotating. It revolves around the axis. Due to the revolving swivel motion of the movable scroll 3, the fluid (refrigerant gas) flows from the suction port via the suction chamber 9 and the fluid passage space 11 to the first compression chamber C1 and the first compression chamber C1 between the fixed lap 2b and the movable lap 3b of the scroll unit 4. 2 It is taken into the compression chamber C2.
  • the extension angle ⁇ 1 up to the winding end end 2f of the fixed wrap 2b is smaller than the extension angle ⁇ 2 up to the winding end end 3f of the movable wrap 3b. Therefore, as shown in FIG. 7, after the first compression chamber C1 is sealed by the contact between the winding end end 3f of the movable wrap 3b and the outer wall surface 2b2 of the fixed wrap 2b, as shown in FIG. The second compression chamber C2 is sealed by the contact between the winding end end 2f of the fixed wrap 2b and the outer wall surface 3b2 of the movable wrap 3b.
  • the first compression chamber C1 always compresses the fluid ahead of the second compression chamber C2, so that the pressure in the first compression chamber C1 is always higher than the pressure in the second compression chamber C2. (Refer to the crank angle of 0 ° to 360 ° in FIG. 12). Therefore, the generated rotation moment is always larger than that of the conventional scroll compressor (see FIG. 13). The direction of this rotation moment coincides with the direction of the revolution turning motion of the movable scroll 3.
  • the fluid compressed by the reduction change in the volume of the first compression chamber C1 due to the orbital turning motion of the movable scroll 3 is located in the central portion via the recess 3h of the movable lap 3b. It mixes with the fluid in the third compression chamber C3. That is, after the operating state shown in FIG. 9, the first compression chamber C1 communicates with the third compression chamber C3 via the recess 3h of the movable lap 3b.
  • the third compression chamber C3 includes the discharge hole 14 and is surrounded by the fixed lap 2b and the movable lap 3b. At the time of this operating state, the discharge valve 15 is closed, and the pressure in the third compression chamber C3 is higher than the pressure in the first compression chamber C1.
  • the high-pressure fluid in the third compression chamber C3 flows into the first compression chamber C1 through the recess 3h of the movable lap 3b. (Backflow).
  • the pressure in the first compression chamber C1 rises sharply (see the crank angle ⁇ in FIGS. 12 and 13).
  • the crank angle ⁇ is 310 °, but the crank angle ⁇ is not limited to this value. Therefore, the sudden increase in the pressure in the first compression chamber C1 at the crank angle ⁇ increases the difference between the pressure in the first compression chamber C1 and the pressure in the second compression chamber C2 (crank angle ⁇ in FIG. 12). See ⁇ 360 °). Therefore, as shown in FIG. 13, the decrease in the rotation moment at the crank angle ⁇ to 360 ° can be suppressed as compared with the conventional scroll compressor.
  • the fluid compressed by the contraction change of the volume of the second compression chamber C2 due to the revolution turning motion of the movable scroll 3 is the first compression chamber C1 to which the third compression chamber C3 is combined. Mix with the fluid inside. That is, immediately after the operating state shown in FIG. 10, the first compression chamber C1, the second compression chamber C2, and the third compression chamber C3 are combined to form the final compression chamber C4, so that the second compression chamber C2 is formed. Communicate with the discharge hole 14.
  • FIG. 12 shows how the fluid in the final compression chamber C4 is compressed and the pressure rises after the crank angle of 360 °.
  • the discharge valve 15 opens, and the fluid in the final compression chamber C4 is discharged to the discharge chamber 13 through the discharge hole 14.
  • the center of the movable bottom plate 3a and the center 3d of the base circle 3c of the movable lap 3b are eccentric to each other.
  • the distance L (not shown) between the center of the compression reaction force acting on the movable scroll 3 and the center of the movable bottom plate 3a fluctuates during one turn of the movable scroll 3.
  • the center of the compression reaction force acting on the movable scroll 3 is at the midpoint between the center 2d of the base circle 2c and the center 3d of the base circle 3c if the first compression chamber C1 and the second compression chamber C2 have the same pressure. ..
  • the above-mentioned distance L becomes larger
  • the center of the compression reaction force approaches the center of the movable bottom plate 3a (that is, the above-mentioned distance L becomes smaller).
  • the above-mentioned distance L becomes the minimum in the vicinity of the crank angles 0 °, 360 °, and 720 ° shown in FIGS. 12 and 13.
  • the above-mentioned rotation moment is a moment around the center of the movable bottom plate 3a, and is the product of the compression reaction force and the above-mentioned distance L.
  • the compression reaction force fluctuates during one turn of the movable scroll 3, and becomes the minimum near, for example, the crank angles of 0 °, 360 °, and 720 ° shown in FIGS. 12 and 13. Therefore, since the crank angle that minimizes the above-mentioned distance L and the crank angle that minimizes the compression reaction force are close to each other, the rotation moment decreases at that angle (near the crank angles 0 °, 360 °, and 720 °). Is a concern.
  • the extension angle ⁇ 1 up to the winding end end 2f of the fixed wrap 2b is made smaller than the extension angle ⁇ 2 up to the winding end end 3f of the movable lap 3b.
  • the first compression chamber C1 always compresses the fluid ahead of the second compression chamber C2, the pressure in the first compression chamber C1 is always higher than the pressure in the second compression chamber C2. (See FIG. 12 for a crank angle of 0 ° to 360 °), and as a result, the generated rotation moment can be raised (see FIG. 13).
  • the scroll compressor 1 includes a fixed bottom plate 2a having a discharge hole 14 in the center, a fixed scroll 2 having a spiral fixed wrap 2b erected on the fixed bottom plate 2a, and a movable bottom plate. It is formed by a movable scroll 3 having a movable bottom plate 3a and a spiral movable lap 3b that is erected on the movable bottom plate 3a and meshes with the fixed lap 2b, and an inner wall surface 3b1 of the movable lap 3b and an outer wall surface 2b2 of the fixed lap 2b.
  • the first compression chamber C1, the second compression chamber C2 formed by the inner wall surface 2b1 of the fixed lap 2b and the outer wall surface 3b2 of the movable lap 3b, and the rotation prevention mechanism 30 for preventing the rotation of the movable scroll 3 are provided.
  • the volume of the first compression chamber C1 and the volume of the second compression chamber C2 are adjusted by rotating the movable scroll 3 around the axis of the fixed scroll 2 while preventing the movable scroll 3 from rotating by the rotation prevention mechanism 30.
  • the fixed lap 2b can be formed by an involute curve based on the base circle 2c of the fixed lap 2b.
  • the movable lap 3b can be formed by an involute curve based on the base circle 3c of the movable lap 3b.
  • the extension angle ⁇ 1 from the reference point 2e on the base circle 2c of the fixed lap 2b to the winding end end 2f of the fixed lap 2b is the winding end end of the movable lap 3b from the reference point 3e on the base circle 3c of the movable lap 3b. It is smaller than the extension angle ⁇ 2 up to the portion 3f.
  • the first compression chamber C1 is sealed by the contact between the winding end end 3f of the movable wrap 3b and the outer wall surface 2b2 of the fixed wrap 2b, the winding end end 2f of the fixed wrap 2b and the movable wrap 3b
  • the second compression chamber C2 is sealed by coming into contact with the outer wall surface 3b2. Therefore, since the pressure in the first compression chamber C1 is always higher than the pressure in the second compression chamber C2, the rotation moment can always be generated in the movable scroll 3, and the decrease in the rotation moment is suppressed. can do.
  • the movable wrap 3b has a recess 3h formed in the winding start end 3g of the movable wrap 3b and recessed with respect to the inner wall surface 3b1 of the winding start end 3g.
  • the scroll compressor 1 further includes a third compression chamber C3 that includes a discharge hole 14 and is surrounded by a fixed lap 2b and a movable lap 3b. After the first compression chamber C1 communicates with the third compression chamber C3 through the recess 3h of the movable wrap 3b, the second compression chamber C2 communicates with the discharge hole 14. As a result, the difference between the pressure in the first compression chamber C1 and the pressure in the second compression chamber C2 can be increased, and the decrease in the rotation moment can be suppressed.
  • the rotation prevention mechanism 30 is provided on the ring 31 which is press-fitted into a circular hole formed in one of the back surface of the movable bottom plate 3a and the housing wall facing the back surface, and the other. Includes a pin 32 that is loosely fitted inside the ring 31. It is possible to suppress the generation of vibration and noise in the rotation prevention mechanism 30 having such a configuration.
  • the center of the fixed bottom plate 2a and the center 2d of the base circle 2c of the fixed wrap 2b are eccentric to each other.
  • the center of the movable bottom plate 3a and the center 3d of the base circle 3c of the movable lap 3b are eccentric to each other. In the scroll compressor 1 having such a configuration, it is possible to suppress the generation of vibration and noise in the rotation prevention mechanism 30.
  • the external drive source for driving the scroll compressor 1 of the present embodiment may be a vehicle engine, a motor, or the like. Further, the scroll compressor 1 may be integrated with a motor as a drive source.
  • the scroll compressor 1 of the present embodiment may be incorporated into, for example, a refrigerant circuit of a vehicle air conditioner, and may be configured to compress and discharge the refrigerant sucked from the low pressure side of the refrigerant circuit.
  • the scroll unit 4 (fixed scroll 2 and movable scroll 3) described above can also be applied to a scroll expander.
  • This scroll expander may be, for example, incorporated into a refrigerant circuit of a vehicle Rankine cycle device, and may be configured to expand a refrigerant introduced from the refrigerant circuit to generate power (recover power from the refrigerant).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2021/038215 2020-11-24 2021-10-15 スクロール圧縮機 WO2022113559A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US18/251,994 US20240011488A1 (en) 2020-11-24 2021-10-15 Scroll compressor
CN202180076524.7A CN116457577A (zh) 2020-11-24 2021-10-15 涡旋式压缩机
DE112021004781.7T DE112021004781T5 (de) 2020-11-24 2021-10-15 Scrollkompressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020194330A JP2022083079A (ja) 2020-11-24 2020-11-24 スクロール圧縮機
JP2020-194330 2020-11-24

Publications (1)

Publication Number Publication Date
WO2022113559A1 true WO2022113559A1 (ja) 2022-06-02

Family

ID=81754256

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2021/038215 WO2022113559A1 (ja) 2020-11-24 2021-10-15 スクロール圧縮機

Country Status (5)

Country Link
US (1) US20240011488A1 (de)
JP (1) JP2022083079A (de)
CN (1) CN116457577A (de)
DE (1) DE112021004781T5 (de)
WO (1) WO2022113559A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020168483A (ja) * 2020-07-09 2020-10-15 株式会社三洋物産 遊技機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002276570A (ja) * 2002-02-06 2002-09-25 Mitsubishi Heavy Ind Ltd スクロール型流体機械
JP2015059517A (ja) * 2013-09-19 2015-03-30 サンデン株式会社 スクロール型流体機械
JP2016075175A (ja) * 2014-10-03 2016-05-12 サンデンホールディングス株式会社 スクロール型流体機械
JP2017053279A (ja) * 2015-09-10 2017-03-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド スクロール圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002276570A (ja) * 2002-02-06 2002-09-25 Mitsubishi Heavy Ind Ltd スクロール型流体機械
JP2015059517A (ja) * 2013-09-19 2015-03-30 サンデン株式会社 スクロール型流体機械
JP2016075175A (ja) * 2014-10-03 2016-05-12 サンデンホールディングス株式会社 スクロール型流体機械
JP2017053279A (ja) * 2015-09-10 2017-03-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド スクロール圧縮機

Also Published As

Publication number Publication date
JP2022083079A (ja) 2022-06-03
DE112021004781T5 (de) 2023-06-29
US20240011488A1 (en) 2024-01-11
CN116457577A (zh) 2023-07-18

Similar Documents

Publication Publication Date Title
JP4535885B2 (ja) スクロール型流体機械
EP3418575B1 (de) Verdichter mit integrierter strömungspfadstruktur
JP6207942B2 (ja) スクロール型流体機械
JP2010190074A (ja) スクロール型流体機械
WO2010125961A1 (ja) スクロール圧縮機
JP2012052527A (ja) スクロール型流体機械
WO2022113559A1 (ja) スクロール圧縮機
JP4884904B2 (ja) 流体機械
JP5914810B2 (ja) スクロール型圧縮機
JP6899230B2 (ja) スクロール型流体機械
WO2016043132A1 (ja) スクロール型流体機械
JP2009127524A (ja) スクロール圧縮機
JP2018071480A (ja) スクロール型流体機械
JPWO2018003032A1 (ja) スクロール圧縮機
JP4094504B2 (ja) スクロール型圧縮機
JP6718223B2 (ja) スクロール流体機械
WO2022130893A1 (ja) スクロール型圧縮機
JP3074980B2 (ja) スクロール型圧縮機
JP5455287B2 (ja) 圧縮機
JP3124161B2 (ja) 密閉型圧縮機
JP4875474B2 (ja) スクロール型流体機械
JPS63159689A (ja) スクロ−ル圧縮機
JP2011169284A (ja) スクロール型圧縮機
JP6425487B2 (ja) スクロール型流体機械
JPH09126164A (ja) スクロール型流体装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21897537

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 18251994

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 202180076524.7

Country of ref document: CN

122 Ep: pct application non-entry in european phase

Ref document number: 21897537

Country of ref document: EP

Kind code of ref document: A1