WO2018163233A1 - Compresseur à spirale et dispositif à cycle de réfrigération - Google Patents

Compresseur à spirale et dispositif à cycle de réfrigération Download PDF

Info

Publication number
WO2018163233A1
WO2018163233A1 PCT/JP2017/008719 JP2017008719W WO2018163233A1 WO 2018163233 A1 WO2018163233 A1 WO 2018163233A1 JP 2017008719 W JP2017008719 W JP 2017008719W WO 2018163233 A1 WO2018163233 A1 WO 2018163233A1
Authority
WO
WIPO (PCT)
Prior art keywords
pair
scroll
oldham
key portions
fixed
Prior art date
Application number
PCT/JP2017/008719
Other languages
English (en)
Japanese (ja)
Inventor
森田　慎也
石園　文彦
友寿 松井
修平 小山
祐司 ▲高▼村
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2017/008719 priority Critical patent/WO2018163233A1/fr
Priority to JP2019503826A priority patent/JP6678811B2/ja
Publication of WO2018163233A1 publication Critical patent/WO2018163233A1/fr

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

Definitions

  • the present invention relates to a scroll compressor and a refrigeration cycle apparatus in which relative phase alignment is performed between a fixed scroll and an orbiting scroll.
  • the swing scroll is supported by a frame fixed to the inner wall of the shell.
  • a fixed scroll is provided at a position facing the swing scroll.
  • a crankshaft is attached to the orbiting scroll. As the crankshaft rotates, the swinging scroll swings with respect to the fixed scroll. By this swinging motion, the refrigerant is compressed in a compression chamber formed by combining the swing scroll and the fixed scroll.
  • the fixed scroll and the orbiting scroll forming the compression chamber maintain a mutual phase relationship with respect to the frame. That is, the phase relationship between the fixed scroll and the frame is determined using a reamer pin or the like.
  • the fixed scroll whose phase relationship is determined is fixed to the frame by bolt fastening.
  • the phase relationship between the orbiting scroll and the frame is determined by a connecting member such as an Oldham ring.
  • the orbiting scroll whose phase relationship is determined is accommodated in the frame.
  • the fixed scroll and the orbiting scroll perform the relative phase alignment indirectly through the frame (for example, see Patent Document 1).
  • the fixed scroll and the orbiting scroll which require high phase relationship accuracy, indirectly perform relative phase alignment via the frame, which increases the number of parts and makes the assembly complicated and increases costs. Will occur.
  • the present invention has been made to solve the above-mentioned problems, and a scroll compressor and a refrigeration cycle in which a fixed scroll and an orbiting scroll can directly perform relative phase alignment by an Oldham ring and the degree of freedom in designing an orbiting scroll can be improved.
  • An object is to provide an apparatus.
  • a scroll compressor includes a fixed scroll and an orbiting scroll in which respective plate-like spiral teeth are engaged to form a compression chamber, an Oldham ring for preventing the orbiting scroll from rotating, and the orbiting scroll.
  • a frame that rotatably supports a driving main shaft, and a shell that is a casing in which the fixed scroll, the orbiting scroll, the Oldham ring, and the frame are provided, and the fixed scroll includes a pair of A pair of second Oldham grooves, and the Oldham ring is inserted into and accommodated in each of the pair of first Oldham grooves of the fixed scroll.
  • a pair of second keys that are inserted into and housed in each of the pair of second Oldham grooves of the orbiting scroll. It includes a part, the said fixed scroll and said frame is one that is fixed to the shell.
  • a refrigeration cycle apparatus includes the scroll compressor described above.
  • the Oldham ring is inserted into each of the pair of first Oldham grooves of the fixed scroll, and the pair of swinging scrolls. And a pair of second key portions that are inserted into and accommodated in each of the second Oldham grooves.
  • the fixed scroll and the frame were fixed to the shell. Therefore, the relative phase of the fixed scroll and the swing scroll can be directly adjusted by the Oldham ring, the degree of freedom of design of the swing scroll can be improved, and the cost can be reduced.
  • FIG. 1 is an exploded perspective view showing a scroll compressor according to Embodiment 1 of the present invention. It is a perspective view which shows the fixed scroll in the scroll compressor which concerns on Embodiment 1 of this invention. It is a perspective view which shows the rocking scroll in the scroll compressor which concerns on Embodiment 1 of this invention. It is a top view which shows the 2nd board
  • FIG. 1 It is an enlarged view which shows the area
  • FIG. 10 is a schematic diagram collectively showing the positional relationship of one rotation of the main frame, thrust plate, Oldham ring, and orbiting scroll in the scroll compressor according to Embodiment 1 of the present invention.
  • FIG. 15 is a schematic diagram collectively showing a positional relationship of one rotation of the main frame, Oldham ring, and orbiting scroll in the scroll compressor according to the second embodiment of the present invention
  • It is a refrigerant circuit figure which shows the refrigerating-cycle apparatus to which the scroll compressor which concerns on Embodiment 4 of this invention is applied.
  • FIG. 1 is a schematic configuration diagram showing a scroll compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 2 is a schematic configuration diagram showing a state in which the phase of the scroll compressor 100 according to Embodiment 1 of the present invention is changed by 90 ° from FIG.
  • FIG. 3 is an exploded perspective view showing the scroll compressor 100 according to Embodiment 1 of the present invention.
  • the scroll compressor 100 shown in FIG. 1 is a so-called vertical scroll compressor that is used in a state where the central axis of the crankshaft 6 is perpendicular to the ground.
  • the scroll compressor 100 includes a shell 1, a main frame 2, a compression mechanism portion 3, a drive mechanism portion 4, a subframe 5, a crankshaft 6, a slider balancer 7, and a power feeding portion 8. Yes.
  • the main frame 2 is used as a reference, and the upper side where the compression mechanism unit 3 is provided is oriented as one end side U and the lower side where the drive mechanism unit 4 is provided is oriented as the other end side L.
  • the shell 1 is a cylindrical casing made of a metal member and closed at both ends, and includes a main shell 11, an upper shell 12, and a lower shell 13.
  • the main shell 11 has a cylindrical shape, and a suction pipe 14 is connected to the side wall thereof by welding or the like.
  • the suction pipe 14 is a pipe for introducing a refrigerant into the shell 1 and communicates with the main shell 11.
  • the upper shell 12 is a first shell having a substantially hemispherical shape. A part of the side wall of the upper shell 12 is connected to the upper end portion of the main shell 11 by welding or the like, and covers the upper opening of the main shell 11.
  • a discharge pipe 15 is connected to the upper part of the upper shell 12 by welding or the like. The discharge pipe 15 is a pipe for discharging the refrigerant to the outside of the shell 1 and communicates with the internal space of the main shell 11.
  • the lower shell 13 is a second shell having a substantially hemispherical shape. A part of the side wall of the lower shell 13 is connected to the lower end of the main shell 11 by welding or the like, and covers the lower opening of the main shell 11.
  • the lower shell 13 is supported by a fixed base 17 having a plurality of holes. A plurality of holes are formed in the fixed base 17.
  • the scroll compressor 100 can be fixed to another member such as a casing of the outdoor unit through the plurality of holes.
  • the main frame 2 is a hollow metal frame in which a cavity is formed, and is provided inside the shell 1 that is a housing.
  • the main frame 2 rotatably supports the crankshaft 6 that drives the orbiting scroll 32.
  • the main frame 2 includes a main body portion 21, a main bearing portion 22, and an oil return pipe 23.
  • the main body 21 is fixed to the inner wall surface on one end side U of the main shell 11.
  • An accommodation space 211 is formed in the center of the main body 21 along the longitudinal direction of the shell 1.
  • one end side U is open, and the space becomes narrower toward the other end side L.
  • An annular flat thrust surface 212 is formed on one end side U of the main body 21 so as to surround the accommodation space 211.
  • On the thrust surface 212 a ring-shaped thrust plate 24 made of a steel plate material is disposed. Therefore, the thrust plate 24 functions as a thrust bearing.
  • a suction port 213 is formed at a position that does not overlap the thrust plate 24 on the outer end side of the thrust surface 212.
  • the suction port 213 is a space penetrating in the vertical direction of the main body 21, that is, the upper shell 12 side and the lower shell 13 side.
  • the main bearing portion 22 is formed continuously on the other end side L of the main body portion 21.
  • a shaft hole 221 is formed in the main bearing portion 22.
  • the shaft hole 221 passes through the main bearing portion 22 in the vertical direction.
  • One end U of the shaft hole 221 communicates with the accommodation space 211.
  • the oil return pipe 23 is a pipe that returns the lubricating oil accumulated in the accommodation space 211 to the oil sump inside the lower shell 13.
  • the oil return pipe 23 is inserted and fixed in an oil drain hole formed through the main frame 2 in and out.
  • Lubricating oil is stored in the lower part of the shell 1, that is, in the lower shell 13, and is sucked up by the crankshaft 6.
  • the sucked lubricating oil reduces the wear of mechanically contacting parts such as the compression mechanism section 3, improves the temperature control of the sliding section, and improves the sealing performance.
  • As the lubricating oil an oil having an appropriate viscosity as well as excellent lubrication characteristics, electrical insulation, stability, refrigerant solubility, low-temperature fluidity and the like is suitable.
  • the compression mechanism unit 3 is a scroll compression mechanism that includes a fixed scroll 31, an orbiting scroll 32, and an Oldham ring 33 in order to compress the refrigerant.
  • the fixed scroll 31, the swing scroll 32, and the Oldham ring 33 are provided inside the shell 1 that is a casing.
  • FIG. 4 is a perspective view showing fixed scroll 31 in scroll compressor 100 according to Embodiment 1 of the present invention.
  • the fixed scroll 31 includes a first substrate 311 and a first spiral body 312.
  • the first substrate 311 is formed in a disk shape.
  • a discharge port 313 is formed in the center of the first substrate 311 so as to penetrate in the vertical direction.
  • the first spiral body 312 protrudes from the surface on the other end side L of the first substrate 311 to form a spiral wall.
  • the tip of the first spiral body 312 protrudes to the other end L.
  • a first Oldham groove 314 is formed on the surface of the first substrate 311.
  • the first Oldham groove 314 is a rectangular groove.
  • the first Oldham groove 314 is provided so that a pair faces the axis of the crankshaft 6.
  • the first Oldham groove 314 is formed in a space long in the radial direction.
  • FIG. 5A is a perspective view showing orbiting scroll 32 in scroll compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 5B is a top view showing second substrate 321 of orbiting scroll 32 in scroll compressor 100 according to Embodiment 1 of the present invention.
  • the swing scroll 32 includes a second substrate 321, a second spiral body 322, a tubular portion 323, and a second Oldham groove 324.
  • the second substrate 321 is located on the one end side U surface on which the first spiral body 312 is formed, on the other end side L surface on which at least a part of the outer peripheral region is a sliding surface, and on the outermost portion in the radial direction. And a side surface connecting both surfaces of the one end U side and the other end L side.
  • the sliding surface of the second substrate 321 is supported by the main frame 2 so as to be slidable on the thrust plate 24.
  • the second spiral body 322 protrudes from the surface on one end side U of the second substrate 321 to form a spiral wall.
  • the tip of the second spiral body 322 protrudes to one end side U.
  • a seal member that suppresses refrigerant leakage is provided at the tip of the first spiral body 312 of the fixed scroll 31 and the tip of the second spiral body 322 of the orbiting scroll 32.
  • the cylindrical portion 323 is a cylindrical boss formed so as to protrude from the approximate center of the surface on the other end L side of the second substrate 321 to the other end L.
  • a swing bearing that supports the slider 71 in a freely rotatable manner, a so-called journal bearing is provided.
  • the center axis of the journal bearing is set parallel to the axis of the crankshaft 6.
  • a second Oldham groove 324 is formed on the surface on the other end side L of the second substrate 321.
  • the second Oldham groove 324 is a rectangular groove.
  • the second Oldham groove 324 is provided so that a pair faces the axis of the crankshaft 6.
  • the second Oldham groove 324 is formed in a space long in the radial direction.
  • the third imaginary line connecting the pair of first Oldham grooves 314 and the fourth imaginary line connecting the pair of second Oldham grooves 324 are orthogonal to each other on a plane orthogonal to the axial direction of the main shaft portion 61 of the crankshaft.
  • Two U-shaped cutout portions 325 are provided on the second substrate 321 of the orbiting scroll 32 so as to face each other.
  • the notch 325 is formed at a position that does not always block the suction port 213 of the main frame 2 and does not interfere with the Oldham ring 33 during compressor operation. A detailed opening range of the notch 325 will be described later.
  • An Oldham ring 33 is provided in the Oldham accommodating portion 214 of the main frame 2. That is, the Oldham ring 33 is accommodated in the Oldham accommodating portion 214 in the main frame 2 that is located on the opposite side of the fixed scroll 31 with respect to the swing scroll 32. The Oldham ring 33 prevents the swing scroll 32 from rotating.
  • the Oldham ring 33 includes an annular part 331, a pair of arm parts 334, a pair of first key parts 332, and a pair of second key parts 333.
  • the annular portion 331 has a ring shape, and is provided with a pair of arm portions 334 that are respectively connected to the pair of first key portions 332.
  • the pair of arm portions 334 extends radially outward with respect to the axis of the crankshaft 6.
  • the first key portion 332 is formed on the surface on one end side U of the pair of arm portions 334 extending from the annular portion 331. That is, the Oldham ring 33 is provided on each of the pair of arm portions 334 in which each of the pair of first key portions 332 extends from the annular portion 331 outward in the radial direction.
  • the pair of first key portions 332 are inserted and accommodated in the pair of first Oldham grooves 314 of the fixed scroll 31, respectively.
  • the pair of first key portions 332 extend through each of the pair of notch portions 325 of the orbiting scroll 32 so as to be inserted and accommodated in each of the pair of first Oldham grooves 314.
  • the second key portion 333 is formed so that a pair faces the surface on one end side U of the annular portion 331. That is, the Oldham ring 33 is provided with a pair of second key portions 333 in the annular portion 331.
  • the pair of second key portions 333 are inserted and accommodated in the pair of second Oldham grooves 324 of the swing scroll 32.
  • the pair of second key portions 333 are extended in the same direction as the pair of first key portions 332 so as to be inserted and accommodated in the pair of second Oldham grooves 324, respectively, and the pair of first key portions 332. It is formed shorter.
  • the pair of second key portions 333 are formed such that the tip ends are longer outside the root portion in the radial direction.
  • the first imaginary line connecting the pair of first key portions 332 and the second imaginary line connecting the pair of second key portions 333 are orthogonal to each other on a plane orthogonal to the axial direction of the main shaft portion 61 of the crankshaft 6.
  • Each of the pair of first Oldham grooves 314 is formed in a space that is longer in the radial direction than each of the pair of first key portions 332 accommodated therein.
  • each of the pair of second Oldham grooves 324 is formed in a space that is longer in the radial direction than each of the pair of second key portions 333 accommodated therein.
  • Each of the pair of second Oldham grooves 324 accommodates each of the pair of second key portions 333 so as to be movable in the radial direction while sliding in the width direction perpendicular to the radial direction. Therefore, the orbiting scroll 32 is held by the crankshaft 6 and the pair of second key portions 333 so as to be able to swing.
  • the first key portion 332 slides in the first Oldham groove 314, and the second key portion 333 slides in the second Oldham groove 324.
  • the Oldham ring 33 prevents the orbiting scroll 32 from rotating.
  • the Oldham ring 33 performs a swinging motion.
  • the compression chamber 34 is formed when the first spiral body 312 of the fixed scroll 31 and the second spiral body 322 of the swing scroll 32 mesh with each other.
  • the compression chamber 34 has a volume that decreases in the radial direction from the outside toward the inside. For this reason, the refrigerant is taken in from the outer ends of the first spiral body 312 and the second spiral body 322 and gradually compressed by moving to the center side.
  • the compression chamber 34 communicates with the discharge port 313 of the fixed scroll 31.
  • a muffler 35 having a discharge hole 351 is provided on the surface of one end U of the fixed scroll 31, and a discharge valve 36 that opens and closes the discharge hole 351 to prevent the refrigerant from flowing backward is provided.
  • the drive mechanism 4 is provided on the other end L of the main frame 2 inside the shell 1.
  • the drive mechanism unit 4 includes a stator 41 and a rotor 42.
  • the stator 41 is a stator formed by winding a winding through an insulating layer on an iron core formed by laminating a plurality of electromagnetic steel plates, for example, and is formed in a ring shape.
  • the stator 41 is fixedly supported inside the main shell 11 by shrink fitting or the like.
  • the rotor 42 is a cylindrical rotor having a built-in permanent magnet inside an iron core formed by laminating a plurality of electromagnetic steel plates and having a through-hole penetrating in the vertical direction in the center, and is disposed in the internal space of the stator 41. ing.
  • the sub frame 5 is a metal frame and is provided inside the shell 1 on the other end side L of the drive mechanism unit 4.
  • the subframe 5 is fixedly supported on the inner peripheral surface of the other end L of the main shell 11 by shrink fitting or welding.
  • the sub frame 5 includes a sub bearing portion 51 and an oil pump 52.
  • the sub-bearing portion 51 is a ball bearing provided on the upper side of the center portion of the sub-frame 5 and has a hole penetrating in the vertical direction at the center.
  • the oil pump 52 is provided below the center portion of the subframe 5 and is disposed so that at least a part of the oil pump 52 is immersed in the lubricating oil stored in the oil reservoir of the shell 1.
  • crankshaft 6 is a long metal rod-like member and is provided inside the shell 1.
  • the crankshaft 6 includes a main shaft portion 61, an eccentric shaft portion 62, and an oil passage 63.
  • the main shaft portion 61 is a shaft constituting the main portion of the crankshaft 6.
  • the central axis of the main shaft portion 61 is disposed so as to coincide with the central axis of the main shell 11.
  • a rotor 42 is fixed in contact with the outer surface of the main shaft portion 61.
  • the eccentric shaft part 62 is provided on one end side U of the main shaft part 61 so that the central axis of the eccentric shaft part 62 is eccentric with respect to the central axis of the main shaft part 61.
  • the oil passage 63 is provided through the main shaft portion 61 and the eccentric shaft portion 62 so as to penetrate vertically.
  • the crankshaft 6 has one end U of the main shaft 61 inserted into the main bearing 22 of the main frame 2 and the other end L inserted and fixed to the sub-bearing 51 of the subframe 5.
  • the eccentric shaft portion 62 is arranged in the cylinder of the cylindrical portion 323, and the outer circumferential surface of the rotor 42 is arranged with a predetermined gap from the inner circumferential surface of the stator 41.
  • a first balancer 64 is provided at one end U of the main shaft portion 61.
  • a second balancer 65 is provided on the other end side L of the main shaft portion 61. The first balancer 64 and the second balancer 65 are provided in order to cancel out the imbalance caused by the swing of the swing scroll 32.
  • the slider balancer 7 includes two parts and includes a slider 71 and a balance weight 72.
  • the slider 71 is a cylindrical member in which a collar is formed, and is fitted into each of the eccentric shaft portion 62 and the cylindrical portion 323.
  • the balance weight 72 is a donut-shaped member provided with a weight portion 721 having a substantially C shape as viewed from one end side U as shown in FIG.
  • the balance weight 72 is provided eccentrically with respect to the rotation center in order to cancel the centrifugal force of the orbiting scroll 32.
  • the balance weight 72 is fitted to the flange of the slider 71 by shrink fitting, for example.
  • the power supply unit 8 is a power supply member that supplies power to the scroll compressor 100, and is formed on the outer peripheral surface of the main shell 11 of the shell 1.
  • the power supply unit 8 includes a cover 81, a power supply terminal 82, and a wiring 83.
  • the cover 81 is a cover member having a bottomed opening.
  • the power supply terminal 82 is made of a metal member, one is provided inside the cover 81, and the other connected from the other is provided inside the shell 1.
  • One of the wires 83 is connected to the power supply terminal 82, and the other connected to one is connected to the stator 41.
  • FIG. 7 is an enlarged view showing a region B indicated by a two-dot chain line in FIG. 6 in the scroll compressor 100 according to Embodiment 1 of the present invention.
  • the shell 1 has a first inner wall surface 111.
  • the shell 1 has a first protrusion 112 that protrudes from the first inner wall surface 111 and positions the fixed scroll 31.
  • the shell 1 has a first positioning surface 113 that faces the upper shell 12 side in the first protrusion 112. That is, the main shell 11 includes a stepped portion whose inner diameter increases toward the other end side L.
  • the fixed scroll 31 is fixed to the first inner wall surface 111 by shrink fitting or the like while being positioned on the first positioning surface 113. That is, the fixed scroll 31 is fixed to the shell 1 which is a housing as a single unit.
  • the main frame 2 is fixed to a shell 1 as a single body as will be described later. As described above, the fixed scroll 31 and the main frame 2 are separately and independently fixed to the shell 1 which is a casing with a space between each other.
  • This structure eliminates the need for a wall for fixing the main frame 2 and the fixed scroll 31 with screws as in the prior art. That is, the wall of the main frame 2 is not interposed between the side surface of the second substrate 321 of the orbiting scroll 32 and the inner wall surface of the main shell 11. The side surface of the second substrate 321 and the inner wall surface of the main shell 11 are arranged to face each other. Therefore, the refrigerant intake space 37 that is provided between the first substrate 311 of the fixed scroll 31 and the thrust bearing of the main frame 2 in the main shell 11 and in which the orbiting scroll 32 is disposed is wider than before.
  • main frame 2 is also fixed to the second inner wall surface 114 by shrink fitting or the like in a state where the main frame 2 is positioned by the second positioning surface of the second protruding portion 115 protruding from the second inner wall surface 114 of the shell 1.
  • FIG. 8 is a perspective view showing the main frame 2 in the scroll compressor 100 according to Embodiment 1 of the present invention.
  • a ring-shaped protruding wall 216 that protrudes toward the upper shell 12 is formed at the outer end portion of the thrust surface 212 of the main frame 2.
  • the thrust plate 24 is disposed so as to cover the thrust surface 212 inside the protruding wall 216.
  • the height of the protruding wall 216 from the thrust surface 212 is set smaller than the thickness of the thrust plate 24. For this reason, the orbiting scroll 32 is slid with the thrust plate 24.
  • the spiral tip gap which is the distance between the substrate of one scroll and the spiral body of the other scroll, can be set within a suitable range.
  • convex portions or concave portions are formed on the thrust plate 24 and the protruding wall 216.
  • a notch 217 capable of suppressing the rotation of the thrust plate 24 is engaged with the convex portion or the concave portion.
  • the thrust plate 24 rotates with respect to the thrust surface 212 as the swing scroll 32 swings. However, the rotation of the thrust plate 24 is suppressed by engaging the convex portion with the concave portion.
  • the recess includes a pair of notches 217 formed in the direction from the protruding wall 216 to the thrust plate 24.
  • the convex portion is constituted by a protruding portion 242 formed on the outer peripheral portion of the thrust plate 24.
  • the pair of notches 217 are provided so as to be locked to the opposing sides of the pair of protrusions 242, respectively.
  • the rotation of the thrust plate 24 is suppressed by two sets of unevenness.
  • the opening 241 of the thrust plate 24 is disposed so as to overlap the pair of suction ports 213 of the main frame 2. That is, the refrigerant passes through the opening 241 and is taken into the refrigerant intake space 37 without being blocked by the thrust plate 24.
  • the opening 241 also serves as the storage space 215 of the Oldham ring 33 described above, and is formed in an opening region where the Oldham ring 33 during operation of the compressor does not interfere.
  • FIG. 9 is a schematic diagram showing a positional relationship among the main frame 2, the thrust plate 24, the Oldham ring 33, and the orbiting scroll 32 in the scroll compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 10 is a schematic diagram collectively showing the positional relationship of one rotation of the main frame 2, the thrust plate 24, the Oldham ring 33, and the orbiting scroll 32 in the scroll compressor 100 according to Embodiment 1 of the present invention.
  • the suction space composed of the suction port 213 and the opening 241 also functions as the suction port and Oldham storage space as described above.
  • the cutout portion 325 of the orbiting scroll 32 is formed so as not to block the suction space during one rotation of the orbiting scroll 32. That is, each of the pair of cutout portions 325 communicates with the suction port 213 of the main frame 2 and is formed in a space that is wider than the respective operating time trajectory ranges of the pair of first key portions 332.
  • the opening area of the notch 325 of the U-shaped orbiting scroll 32 will be described.
  • the notch 325 of the orbiting scroll 32 is preferably formed in a U shape as shown in FIG. 9 so as not to block the suction space with the maximum thrust area.
  • each side of the notch 325 is determined by the size of the suction port 213 of the main frame 2 and the operating range of the orbiting scroll 32.
  • This operating range is determined by design parameters such as the spiral involute curve and tooth thickness of the second spiral body 322 of the orbiting scroll 32. Since it is a well-known technique, description is abbreviate
  • the operating range of the aforementioned orbiting scroll 32 is referred to as a crank radius.
  • the orbiting scroll 32 moves up and down and left and right on the drawing
  • the orbiting scroll 32 moves up and down and left and right on the drawing by the crank radius.
  • the length of the long side of the notch 325 is set to a length that is widened by the crank radius from the opening width in the left-right direction of the suction port 213.
  • the length of the short side of the notch portion 325 needs to be a minimum length that does not interfere with the first key portion 332 of the Oldham ring 33, and the crank radius is determined from the radial length of the thrust surface 212 of the main frame 2. It is set to the extended length.
  • the area of the second substrate 321 of the orbiting scroll 32 is maximized, and the refrigerant is stably sucked into the compression mechanism unit 3 without closing the suction space at any phase during operation. Further, the area of the second substrate 321 is maximized, which leads to an increase in capacity by increasing the configurable area of the second spiral body 322 and an improvement in reliability by maximizing the thrust area.
  • the U-shaped long side and the short side of the cutout portion 325 of the orbiting scroll 32 are preferably perpendicular to each other in accordance with the shape of the suction space. Even if a curved R shape is attached, there is no problem as long as the above-described conditions are satisfied.
  • the notch 325 has a U-shaped opening area. However, it is not limited to this. Instead of the notch, it may be an opening having four sides.
  • the refrigerant sucked into the shell 1 from the suction pipe 14 reaches the refrigerant intake space 37 through the suction port 213 of the main frame 2 and swings with the fixed scroll 31. It is taken into a compression chamber 34 formed by the moving scroll 32. Then, the refrigerant is compressed by reducing the volume while moving from the outer peripheral portion toward the center along with the eccentric revolving motion of the orbiting scroll 32.
  • the orbiting scroll 32 moves in the radial direction together with the slider balancer 7 by its centrifugal force, and the side walls of the second spiral body 322 and the first spiral body 312 are in close contact with each other. To do.
  • the compressed refrigerant reaches the discharge hole 351 of the muffler 35 from the discharge port 313 of the fixed scroll 31 and is discharged outside the shell 1 against the discharge valve 36.
  • the scroll compressor 100 includes the fixed scroll 31 and the orbiting scroll 32 that form the compression chamber 34 by meshing the respective plate-like spiral teeth.
  • the scroll compressor 100 includes an Oldham ring 33 that prevents the swinging scroll 32 from rotating.
  • the scroll compressor 100 includes a main frame 2 that rotatably supports the crankshaft 6 that drives the orbiting scroll 32.
  • the scroll compressor 100 includes a shell 1 that is a casing in which a fixed scroll 31, an orbiting scroll 32, an Oldham ring 33, and a main frame 2 are provided.
  • the fixed scroll 31 has a pair of first Oldham grooves 314.
  • the swing scroll 32 has a pair of second Oldham grooves 324.
  • the Oldham ring 33 has a pair of first key portions 332 that are inserted into and housed in the pair of first Oldham grooves 314 of the fixed scroll 31.
  • the Oldham ring 33 has a pair of second key portions 333 that are inserted and accommodated in the pair of second Oldham grooves 324 of the swing scroll 32.
  • the fixed scroll 31 and the main frame 2 are respectively fixed to the shell 1. According to this configuration, the fixed scroll 31 and the swing scroll 32 can directly perform relative phase alignment by the Oldham ring 33.
  • the fixed scroll 31 and the main frame 2 are separately and independently fixed to the shell 1 that is a casing. Thereby, the wall of the main frame 2 for fixing the fixed scroll 31 which was conventionally required can be deleted.
  • the Oldham ring 33 is the minimum necessary component. Therefore, the space of the compression chamber 34 that can be formed between the fixed scroll 31 and the main frame 2 can be effectively used, and the degree of freedom in designing the orbiting scroll 32 can be improved. Further, the number of parts can be reduced, the assembly can be simplified, and the cost can be reduced. In addition, a large space can be formed between the fixed scroll 31 and the main frame 2.
  • the area of the second substrate 321 of the orbiting scroll 32 can be utilized to the maximum, the configurable area of the plate-like spiral teeth can be increased, the plate-like spiral teeth can be increased in capacity, and the thrust area can be expanded,
  • the swing motion of the swing scroll 32 can be stabilized and the reliability can be improved.
  • the Oldham ring 33 is accommodated in the main frame 2 located on the opposite side of the fixed scroll 31 with respect to the orbiting scroll 32.
  • the rocking scroll 32 has a pair of notch portions 325.
  • the pair of first key portions 332 extends through each of the pair of notch portions 325 of the swing scroll 32 and is inserted and accommodated in each of the pair of first Oldham grooves 314 of the fixed scroll 31.
  • the pair of second key portions 333 extend in the same direction as the pair of first key portions 332, are shorter than the pair of first key portions 332, and are formed on the pair of second Oldham grooves 324 of the orbiting scroll 32. It is inserted and accommodated in each.
  • the fixed scroll 31 and the swing scroll 32 can directly perform relative phase alignment by the Oldham ring 33.
  • a larger space without the Oldham ring 33 can be formed between the fixed scroll 31 and the main frame 2.
  • the area of the second substrate 321 of the orbiting scroll 32 can be utilized to the maximum, the configurable area of the plate-like spiral teeth can be increased, the plate-like spiral teeth can be increased in capacity, and the thrust area can be expanded,
  • the swing motion of the swing scroll 32 can be stabilized and the reliability can be improved.
  • each of the pair of cutout portions 325 communicates with the suction port 213 of the main frame 2 and has a space wider than the respective operating trajectory ranges of the pair of first key portions 332. Is formed. According to this configuration, each of the pair of notch portions 325 does not interfere with the movement of each of the pair of first key portions 332, and the swinging motion of the swing scroll 32 can be performed smoothly. In addition, each of the pair of notch portions 325 is a space having a wider area than the respective operating trajectory range of the pair of first key portions 332. For this reason, a gap is generated between each edge of the pair of cutout portions 325 and each of the pair of first key portions 332, and the refrigerant can be guided from the suction port 213 of the main frame 2 to the compression chamber 34.
  • the Oldham ring 33 is provided on each of the pair of arm portions 334 in which each of the pair of first key portions 332 extends from the annular portion 331 to the outside in the radial direction.
  • a second key portion 333 is provided in the annular portion 331.
  • each of the pair of first key portions 332 is provided on each of the pair of arm portions 334, so that the area where the plate-like spiral teeth of the orbiting scroll 32 can be configured is not reduced. It can be accommodated in each of the grooves 314. Thereby, the fixed scroll 31 and the swing scroll 32 can directly perform relative phase alignment by the Oldham ring 33.
  • the first imaginary line connecting the pair of first key portions 332 and the second imaginary line connecting the pair of second key portions 333 are orthogonal on a plane orthogonal to the axial direction of the crankshaft 6. is doing. According to this configuration, the pair of first key portions 332 and the pair of second key portions 333 do not interfere with each other in the moving direction, and the swing motion of the swing scroll 32 can be performed smoothly.
  • each of the pair of first Oldham grooves 314 is formed in a space that is longer in the radial direction than each of the pair of first key portions 332 accommodated therein.
  • Each of the pair of second Oldham grooves 324 is formed in a space longer in the radial direction than each of the pair of second key portions 333 accommodated.
  • each of the pair of first key portions 332 is accommodated in each of the pair of first Oldham grooves 314 and can slide smoothly.
  • each of the pair of second key portions 333 is accommodated in each of the pair of second Oldham grooves 324 and can slide smoothly. Thereby, the swing motion of the swing scroll 32 can be performed smoothly.
  • the fixed scroll 31 and the main frame 2 are respectively fixed to the shell 1 that is a casing. According to this configuration, the fixed scroll 31 and the main frame 2 are fixed to the shell 1 separately. Thereby, the wall of the main frame 2 for fixing the fixed scroll 31 which was conventionally required can be deleted. In addition, a bolt for fastening the fixed scroll 31 and the main frame 2 becomes unnecessary. In addition, since the phase relationship between the fixed scroll 31 and the orbiting scroll 32 is maintained, only the Oldham ring 33 is the minimum necessary component. Therefore, the space of the compression chamber 34 can be used effectively, and the degree of freedom in designing the orbiting scroll 32 can be improved. Further, the number of parts can be reduced, the assembly can be simplified, and the cost can be reduced.
  • Embodiment 2 FIG. Next, a second embodiment will be described. In the second embodiment, the description of the same configuration described in the first embodiment will be omitted, and only the characteristic part will be described.
  • FIG. 11 is a schematic configuration diagram showing an upper half of the scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 12 is a schematic configuration diagram showing a state where the phase of the upper half of the scroll compressor 100 according to Embodiment 2 of the present invention is changed by 90 ° from FIG.
  • FIG. 13 is an exploded perspective view showing the scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 14 is a schematic diagram showing a positional relationship among the main frame 2, the Oldham ring 33, and the orbiting scroll 32 in the scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 11 is a schematic configuration diagram showing an upper half of the scroll compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 12 is a schematic configuration diagram showing a state where the phase of the upper half of the scroll compressor 100 according to Embodiment 2 of the present invention is changed by 90 ° from FIG.
  • FIG. 13 is an exploded perspective view showing the scroll compressor 100 according to Em
  • FIG. 15 is a schematic view collectively showing the positional relationship of one rotation of the main frame 2, the Oldham ring 33, and the swinging scroll 32 in the scroll compressor 100 according to Embodiment 2 of the present invention.
  • Is a schematic diagram showing the positional relationship of ⁇ 0 °
  • FIG. 15D is a schematic diagram
  • the Oldham ring 33 is housed in the Oldham housing portion 214 in the main frame 2 located on the opposite side of the fixed scroll 31 with respect to the orbiting scroll 32.
  • the pair of first key portions 332 passes through the radially outer side of the orbiting scroll 32 and extends to the one end side U, and is inserted and accommodated in each of the pair of first Oldham grooves 314 of the fixed scroll 31.
  • the pair of second key portions 333 extend in the same direction as the pair of first key portions 332, are formed shorter than the pair of first key portions 332, and are formed on the outer side in the radial direction to be paired with the orbiting scroll 32.
  • Each of the pair of cut out second Oldham grooves 324 is inserted and accommodated.
  • Oldham accommodation part 214 is set inside main frame 2.
  • a thrust surface 212 is set inside the main frame 2.
  • the annular portion 331 of the Oldham ring 33 is enlarged so as to conform to the configuration of the main frame 2 described above.
  • a pair of first key portions 332 and a pair of second key portions 333 are provided on the annular portion 331. That is, the Oldham ring 33 is provided with a pair of first key portions 332 and a pair of second key portions 333 in the annular portion 331.
  • the thrust plate 24 is reduced along the thrust surface 212.
  • the setting condition of the notch 325 of the U-shaped orbiting scroll 32 is the same as that of the first embodiment.
  • the area of the second substrate 321 of the orbiting scroll 32 is maximized, and the capacity can be increased by increasing the configurable area of the second spiral body 322.
  • the Oldham ring 33 is accommodated in the main frame 2 located on the opposite side of the fixed scroll 31 with respect to the swing scroll 32.
  • the pair of first key portions 332 extends through the outer side in the radial direction of the orbiting scroll 32 and is inserted and accommodated in each of the pair of first Oldham grooves 314 of the fixed scroll 31.
  • the pair of second key portions 333 extend in the same direction as the pair of first key portions 332, are shorter than the pair of first key portions 332, and are formed on the pair of second Oldham grooves 324 of the orbiting scroll 32. It is inserted and accommodated in each.
  • the fixed scroll 31 and the swing scroll 32 can directly perform relative phase alignment by the Oldham ring 33.
  • the area of the second substrate 321 of the orbiting scroll 32 can be utilized to the maximum, the configurable area of the plate-like spiral teeth can be increased, the plate-like spiral teeth can be increased in capacity, and the thrust area can be expanded,
  • the swing motion of the swing scroll 32 can be stabilized and the reliability can be improved.
  • the Oldham ring 33 is provided with a pair of first key portions 332 and a pair of second key portions 333 in the annular portion 331. According to this configuration, the locus of movement of the annular portion 331 of the Oldham ring 33 becomes a circular region in which the annular portion 331 is enlarged, and the Oldham ring 33 can be moved smoothly. Further, the relative scroll alignment between the fixed scroll 31 and the swing scroll 32 can be performed directly by the Oldham ring 33.
  • Embodiment 3 FIG. Next, Embodiment 3 will be described.
  • the description of the same configuration described in the first and second embodiments is omitted, and only the characteristic part is described.
  • FIG. 16 is a schematic configuration diagram showing an upper half of the scroll compressor 100 according to Embodiment 3 of the present invention.
  • FIG. 17 is a schematic configuration diagram illustrating a state where the phase of the upper half of the scroll compressor 100 according to the third embodiment of the present invention is changed by 90 ° from FIG. 16.
  • FIG. 18 is an exploded perspective view showing the scroll compressor 100 according to Embodiment 3 of the present invention.
  • the Oldham ring 33 is accommodated between the fixed scroll 31 and the swing scroll 32 in contact with the swing scroll 32.
  • the pair of first key portions 332 is inserted and accommodated in the pair of first Oldham grooves 314 of the fixed scroll 31.
  • the pair of second key portions 333 extends in the opposite direction to the pair of first key portions 332, is formed shorter than the pair of first key portions 332, and includes a pair of second Oldham grooves 324 of the orbiting scroll 32. It is inserted and accommodated in each.
  • the pair of first Oldham grooves 314 formed on the back surface of the fixed scroll 31 and the pair of second Oldham grooves 324 formed on the back surface of the orbiting scroll 32 are engaged by the Oldham ring 33. Combined. For this reason, a highly accurate Oldham ring 33 is required which is large in size and has problems in mass productivity and cost. Further, the thrust bearing provided on the back surface of the orbiting scroll 32 is divided by a pair of arms 334 of the Oldham ring 33 and the like in terms of structure.
  • the Oldham ring 33 is sandwiched between the orbiting scroll 32 and the fixed scroll 31. For this reason, the Oldham ring 33 becomes compact.
  • oil is accumulated on the back surface of the swing scroll 32 as an oil supply path.
  • the sealing performance at the thrust surface 212 which is the contact surface between the upper surface of the main frame 2 and the back surface of the orbiting scroll 32, can be ensured, and oil rising can be suppressed.
  • the thrust bearing has a stable oil supply, can use the entire back surface of the orbiting scroll 32, and has high bearing reliability.
  • the main frame 2 has no wall, and the degree of freedom in the arrangement of the spiral structure can be secured while maintaining the phase accuracy between the orbiting scroll 32 and the fixed scroll 31.
  • the Oldham ring 33 is accommodated in contact with the orbiting scroll 32 between the fixed scroll 31 and the orbiting scroll 32.
  • the pair of first key portions 332 is inserted and accommodated in the pair of first Oldham grooves 314 of the fixed scroll 31.
  • the pair of second key portions 333 extend in the opposite direction to the pair of first key portions 332, and are inserted into and housed in the pair of second Oldham grooves 324 of the orbiting scroll 32.
  • the fixed scroll 31 and the swing scroll 32 can directly perform relative phase alignment by the Oldham ring 33.
  • the Oldham ring 33 becomes compact. In this structure, oil is accumulated on the back surface of the swing scroll 32 as an oil supply path.
  • the sealing performance at the thrust surface 212 which is the contact surface between the upper surface of the main frame 2 and the back surface of the orbiting scroll 32, can be ensured, and oil rising can be suppressed.
  • the thrust bearing has a stable oil supply, can use the entire back surface of the orbiting scroll 32, and has high bearing reliability.
  • the main frame 2 has no wall, and the degree of freedom in the arrangement of the spiral structure can be secured while maintaining the phase accuracy between the orbiting scroll 32 and the fixed scroll 31.
  • the pair of second key portions 333 are formed shorter than the pair of first key portions 332. According to this configuration, the fixed scroll 31 and the swing scroll 32 can directly perform relative phase alignment by the Oldham ring 33. Further, the pair of second key portions 333 are accommodated in the pair of second Oldham grooves 324 that are formed on the surface of the orbiting scroll 32 and do not penetrate through, thereby saving the space of the compression mechanism portion 3.
  • the notch 217 of the main frame 2 and the protrusion 242 of the thrust plate 24 are engaged so as not to rotate.
  • engagement at the concavo-convex portion is not essential.
  • a configuration in which a concave portion is set on the thrust plate 24 side and a convex portion is set on the main frame 2 side may be employed.
  • the thrust plate 24 may be partially bent and locked to an opening such as the suction port 213 of the main frame 2 to prevent rotation.
  • the thrust plate 24 is not an essential component, and the thrust surface 212 of the main frame 2 may slide with the orbiting scroll 32.
  • the suction port 213 of the main frame 2 and the cutout portion 325 of the swing scroll 32 serve as the suction space and the storage space 215 of the first key portion 332 of the Oldham ring 33.
  • the suction port 233 of the main frame 2 and the cutout portion 325 of the orbiting scroll 32 are not connected. The number does not have to be equal.
  • the structure which forms separately the suction space and the space which does not interfere with the 1st key part 332 of the Oldham ring 33 may be sufficient.
  • the area of the second substrate 321 of the orbiting scroll 32 is the largest when the notch 325 of the orbiting scroll 32 is set to be U-shaped.
  • the shape of the cutout portion 325 of the orbiting scroll 32 is not limited to the U shape as long as the suction space is not completely blocked during operation and the first key portion 332 of the Oldham ring 33 is not interfered.
  • the opening illustrated in the notch 325 may be U-shaped, V-shaped, or the like, or a donut-shaped hole such as a round hole or a long hole is formed in the second substrate 321 while the swinging outer peripheral part is connected. A configuration may be used.
  • FIG. 19 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 200 to which the scroll compressor 100 according to Embodiment 4 of the present invention is applied.
  • the refrigeration cycle apparatus 200 includes a scroll compressor 100, a condenser 201, an expansion valve 202, and an evaporator 203.
  • the scroll compressor 100, the condenser 201, the expansion valve 202, and the evaporator 203 are connected by a refrigerant pipe to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 203 is sucked into the scroll compressor 100 and becomes high temperature and pressure.
  • the high-temperature and high-pressure refrigerant is condensed in the condenser 201 to become a liquid.
  • the refrigerant that has become liquid is decompressed and expanded by the expansion valve 202 to form a low-temperature and low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 203.
  • the scroll compressor 100 according to the first to third embodiments can be applied to such a refrigeration cycle apparatus 200.
  • the refrigeration cycle apparatus 200 include an air conditioner, a refrigeration apparatus, and a water heater.
  • the refrigeration cycle apparatus 200 includes the scroll compressor 100 described in the first to third embodiments. According to this configuration, in the refrigeration cycle apparatus 200 including the scroll compressor 100, the fixed scroll 31 and the swing scroll 32 can directly perform relative phase alignment by the Oldham ring 33, and the degree of freedom of design of the swing scroll 32 is improved. Can be improved and the cost can be reduced.

Landscapes

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

Abstract

L'invention concerne un compresseur à spirale pourvu d'une spirale fixe, d'une spirale orbitale, d'une bague d'Oldham, d'un cadre et d'une coque. La spirale fixe a une paire de premières rainures Oldham, la spirale orbitale a une paire de secondes rainures Oldham, la bague d'Oldham comporte une paire de premières parties clavettes qui sont respectivement insérées et logées dans ladite paire de premières rainures d'Oldham de la spirale fixe et une paire de secondes parties clavettes qui sont respectivement insérées et logées dans ladite paire de secondes rainures d'Oldham de la spirale orbitale et la spirale fixe et la spirale orbitale sont respectivement fixées à la coque.
PCT/JP2017/008719 2017-03-06 2017-03-06 Compresseur à spirale et dispositif à cycle de réfrigération WO2018163233A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2017/008719 WO2018163233A1 (fr) 2017-03-06 2017-03-06 Compresseur à spirale et dispositif à cycle de réfrigération
JP2019503826A JP6678811B2 (ja) 2017-03-06 2017-03-06 スクロール圧縮機および冷凍サイクル装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/008719 WO2018163233A1 (fr) 2017-03-06 2017-03-06 Compresseur à spirale et dispositif à cycle de réfrigération

Publications (1)

Publication Number Publication Date
WO2018163233A1 true WO2018163233A1 (fr) 2018-09-13

Family

ID=63447512

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/008719 WO2018163233A1 (fr) 2017-03-06 2017-03-06 Compresseur à spirale et dispositif à cycle de réfrigération

Country Status (2)

Country Link
JP (1) JP6678811B2 (fr)
WO (1) WO2018163233A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020250337A1 (fr) * 2019-06-12 2020-12-17 三菱電機株式会社 Compresseur à spirale et procédé de fabrication de ce compresseur à spirale
WO2021009839A1 (fr) * 2019-07-16 2021-01-21 三菱電機株式会社 Compresseur à volutes
WO2021100153A1 (fr) * 2019-11-20 2021-05-27 三菱電機株式会社 Compresseur à spirale et procédé de fabrication de compresseur à spirale
CN113423952A (zh) * 2019-02-14 2021-09-21 三菱电机株式会社 涡旋压缩机
US12049895B2 (en) * 2021-08-05 2024-07-30 Daikin Industries, Ltd. Scroll compressor and refrigeration cycle apparatus

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11107938A (ja) * 1997-10-01 1999-04-20 Mitsubishi Electric Corp 冷媒圧縮機
JP2002242856A (ja) * 2001-02-14 2002-08-28 Mitsubishi Heavy Ind Ltd スクロール型流体装置
JP2007016790A (ja) * 1993-11-03 2007-01-25 Copeland Corp スクロール型機械

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007016790A (ja) * 1993-11-03 2007-01-25 Copeland Corp スクロール型機械
JPH11107938A (ja) * 1997-10-01 1999-04-20 Mitsubishi Electric Corp 冷媒圧縮機
JP2002242856A (ja) * 2001-02-14 2002-08-28 Mitsubishi Heavy Ind Ltd スクロール型流体装置

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113423952B (zh) * 2019-02-14 2023-09-15 三菱电机株式会社 涡旋压缩机
CN113423952A (zh) * 2019-02-14 2021-09-21 三菱电机株式会社 涡旋压缩机
JPWO2020250337A1 (ja) * 2019-06-12 2021-11-18 三菱電機株式会社 スクロール圧縮機及びそのスクロール圧縮機の製造方法
WO2020250337A1 (fr) * 2019-06-12 2020-12-17 三菱電機株式会社 Compresseur à spirale et procédé de fabrication de ce compresseur à spirale
JP7055245B2 (ja) 2019-06-12 2022-04-15 三菱電機株式会社 スクロール圧縮機及びそのスクロール圧縮機の製造方法
CN113906217A (zh) * 2019-06-12 2022-01-07 三菱电机株式会社 涡旋压缩机以及该涡旋压缩机的制造方法
EP4001650A4 (fr) * 2019-07-16 2022-07-27 Mitsubishi Electric Corporation Compresseur à volutes
JPWO2021009839A1 (fr) * 2019-07-16 2021-01-21
WO2021009839A1 (fr) * 2019-07-16 2021-01-21 三菱電機株式会社 Compresseur à volutes
JP7345550B2 (ja) 2019-07-16 2023-09-15 三菱電機株式会社 スクロール圧縮機
JPWO2021100153A1 (fr) * 2019-11-20 2021-05-27
WO2021100153A1 (fr) * 2019-11-20 2021-05-27 三菱電機株式会社 Compresseur à spirale et procédé de fabrication de compresseur à spirale
JP7150196B2 (ja) 2019-11-20 2022-10-07 三菱電機株式会社 スクロール圧縮機およびスクロール圧縮機の製造方法
US12049895B2 (en) * 2021-08-05 2024-07-30 Daikin Industries, Ltd. Scroll compressor and refrigeration cycle apparatus

Also Published As

Publication number Publication date
JP6678811B2 (ja) 2020-04-08
JPWO2018163233A1 (ja) 2019-06-27

Similar Documents

Publication Publication Date Title
WO2018163233A1 (fr) Compresseur à spirale et dispositif à cycle de réfrigération
JP6678762B2 (ja) スクロール圧縮機、冷凍サイクル装置およびシェル
KR101487022B1 (ko) 압축기
US20190203709A1 (en) Motor-operated compressor
EP2594797B1 (fr) Compresseur pour véhicule
US8366424B2 (en) Rotary fluid machine with reverse moment generating mechanism
US9145890B2 (en) Rotary compressor with dual eccentric portion
JP7118177B2 (ja) スクロール圧縮機
JP2012184709A (ja) スクロール圧縮機
JP6057535B2 (ja) 冷媒圧縮機
WO2019207759A1 (fr) Compresseur à spirale
WO2016157688A1 (fr) Compresseur du type à cylindre rotatif
JP6104396B2 (ja) スクロール圧縮機
WO2023181173A1 (fr) Compresseur à spirale
JP6374737B2 (ja) シリンダ回転型圧縮機
JP7191246B2 (ja) スクロール圧縮機および冷凍サイクル装置
WO2021014641A1 (fr) Compresseur à spirale
JP7313570B2 (ja) スクロール圧縮機
EP4446589A1 (fr) Compresseur à spirale
WO2023100304A1 (fr) Compresseur à spirale
JP7395004B2 (ja) スクロール圧縮機
WO2018150525A1 (fr) Compresseur à spirale
JP2007092738A (ja) 圧縮機
KR20210027061A (ko) 스크롤 압축기
WO2018142536A1 (fr) Compresseur

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: 17899642

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2019503826

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17899642

Country of ref document: EP

Kind code of ref document: A1