WO2016174751A1 - Compresseur - Google Patents

Compresseur Download PDF

Info

Publication number
WO2016174751A1
WO2016174751A1 PCT/JP2015/062892 JP2015062892W WO2016174751A1 WO 2016174751 A1 WO2016174751 A1 WO 2016174751A1 JP 2015062892 W JP2015062892 W JP 2015062892W WO 2016174751 A1 WO2016174751 A1 WO 2016174751A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
spring
vane
insertion hole
axial direction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/062892
Other languages
English (en)
Japanese (ja)
Inventor
勝巳 遠藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2017515334A priority Critical patent/JP6388715B2/ja
Priority to PCT/JP2015/062892 priority patent/WO2016174751A1/fr
Priority to CN201620245576.9U priority patent/CN205714766U/zh
Priority to CN201610183692.7A priority patent/CN106089709A/zh
Publication of WO2016174751A1 publication Critical patent/WO2016174751A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs

Definitions

  • the present invention relates to a compressor that compresses a fluid.
  • Patent Document 1 describes a rotary compressor.
  • This rotary compressor includes a rolling piston, a vane, and a vane spring.
  • the vane spring is accommodated in a spring insertion hole provided in the cylinder.
  • the winding shape of the vane spring and the hole shape of the spring insertion hole are both round.
  • the compression mechanism of the hermetic rotary compressor is fixed by welding a plurality of locations on the outer peripheral surface of the flange portion of the upper bearing or the outer peripheral surface of the rib portion of the cylinder to the sealed container.
  • the cross-sectional area of the bridge portion formed on the back side of the vane groove is reduced.
  • the inner peripheral surface of the cylinder and the vane groove are likely to be distorted. If the distortion of the inner peripheral surface of the cylinder or the vane groove is excessively increased, the airtightness in the compression mechanism is lowered and the compression performance is lowered. Further, since the contact between the cylinder and the sliding component becomes strong, the compressor is likely to fail. Therefore, when the thickness of the cylinder is reduced, the compressor performance cannot be maintained.
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compressor capable of reducing the thickness of a cylinder while maintaining performance.
  • a compressor according to the present invention is in contact with a hollow cylinder housed in a container, a rolling piston that rotates eccentrically along the inner peripheral surface of the cylinder, and an outer peripheral surface of the rolling piston, A vane that divides the space into a suction chamber and a compression chamber; and a vane spring that urges the vane toward the rolling piston.
  • the cylinder has a spring insertion hole into which the vane spring is inserted.
  • the spring insertion hole has a hole shape in which the height dimension in the axial direction of the cylinder is smaller than the width dimension in the tangential direction of the cylinder in at least a part of the spring insertion hole in the axial direction.
  • the vane spring is a coil spring, and the vane spring is at least in the axial direction of the vane spring. In some, in which the height in the axial direction of the cylinder has a smaller winding shape than the width dimension in the tangential direction of the cylinder.
  • the thickness of the cylinder can be reduced while maintaining the performance of the compressor.
  • the general compression mechanism 10 it is a figure which shows collectively the cross-sectional structure in case the thickness of the cylinder 11 is relatively thick, and the cross-sectional structure in case the thickness of the cylinder 11 is relatively thin. It is a perspective view which shows the structure of the cylinder 11 of the compressor 1 which concerns on Embodiment 1 of this invention.
  • FIG. 1 is a longitudinal sectional view showing a schematic configuration of a compressor 1 according to the present embodiment.
  • the compressor 1 is a fluid machine that compresses and discharges a fluid (in this example, a low-pressure gas refrigerant in a refrigeration cycle), and is one of the components of a refrigeration cycle used in, for example, an air conditioner or a refrigerator.
  • a vertical type hermetic rotary compressor is illustrated as the compressor 1 as the compressor 1, a vertical type hermetic rotary compressor is illustrated.
  • the dimensional relationship and shape of each component may differ from the actual ones.
  • the positional relationship (for example, vertical relationship etc.) between each structural member in a specification is a thing when it installs in the state which can use a vertical installation sealed rotary compressor in principle.
  • the compressor 1 includes a compression mechanism 10 that compresses a gas refrigerant and an electric mechanism 50 that drives the compression mechanism 10.
  • the compression mechanism 10 and the electric mechanism 50 are accommodated in the sealed container 60 and fixed to the sealed container 60 by welding or shrink fitting, respectively.
  • Refrigerating machine oil that lubricates the sliding portions of the compressor 1 is stored at the bottom of the sealed container 60.
  • the electric mechanism 50 includes a stator 51 and a rotor 52.
  • the outer peripheral portion of the stator 51 is fixed to the inner peripheral surface of the sealed container 60.
  • a drive shaft 53 is coaxially fixed to the rotor 52.
  • the drive shaft 53 is formed with an eccentric portion 53 a having a central axis at a position shifted from the rotation axis of the drive shaft 53.
  • the compression mechanism 10 is disposed below the electric mechanism 50 in the sealed container 60.
  • the compression mechanism 10 includes a hollow cylinder 11 having a cylindrical opening inside, an upper bearing 12 that is disposed at an upper end in the axial direction of the cylinder 11 and rotatably supports the drive shaft 53, and an axial direction of the cylinder 11.
  • the lower bearing 13 is disposed at the lower end and rotatably supports the drive shaft 53.
  • the upper bearing 12 and the lower bearing 13 also serve as an upper end plate and a lower end plate of the cylinder 11, respectively.
  • a discharge muffler 14 is attached to the upper bearing 12.
  • a discharge muffler chamber is formed between the upper bearing 12 and the discharge muffler 14 to reduce the pulsation of the refrigerant compressed and discharged by the compression mechanism 10.
  • FIG. 2 is a perspective view showing a partial cross-sectional configuration of the compression mechanism 10.
  • the upper bearing 12 is not shown.
  • FIG. 3 is a top view showing the configuration of the cylinder 11.
  • a plurality of rib portions 11 b projecting to the outer peripheral side are formed on the outer peripheral portion of the cylinder 11.
  • the outer peripheral surface 11c of the rib portion 11b (hereinafter sometimes referred to as “the outer peripheral surface 11c of the cylinder 11”) is fixed to the inner peripheral surface of the sealed container 60 by welding or the like.
  • a rolling piston 15 slidably fitted in the eccentric portion 53 a is provided in the space in the cylinder 11.
  • the rolling piston 15 rotates eccentrically along the inner peripheral surface 11a of the cylinder 11 as the eccentric portion 53a rotates.
  • a vane groove 16 is formed from the inner peripheral surface 11 a of the cylinder 11 toward the radially outer side of the cylinder 11.
  • a vane 17 that divides the space in the cylinder 11 into a suction chamber and a compression chamber is accommodated in the vane groove 16 so as to be slidable back and forth.
  • a bridge portion 20 is formed on the back side of the vane groove 16 (that is, between the vane groove 16 and the outer peripheral surface 11 c of the cylinder 11).
  • a spring insertion hole 18 penetrating the bridge portion 20 along the radial direction of the cylinder 11 is formed between the vane groove 16 and the outer peripheral surface 11c of the cylinder 11.
  • a vane spring 19 that urges the vane 17 toward the rolling piston 15 is inserted into the spring insertion hole 18 from the outer peripheral surface 11c side.
  • the vane spring 19 is a compression coil spring. Since the spring insertion hole 18 communicates with the space inside the sealed container 60 outside the cylinder 11, the discharge pressure acts on the back side of the vane 17.
  • the vane 17 is pressed against the outer peripheral surface of the rolling piston 15 by the pressing force due to the pressure difference between the back surface side and the tip end side and the urging force by the vane spring 19. Thereby, the vane 17 reciprocates in the vane groove 16 following the eccentric rotation of the rolling piston 15.
  • the compressor 1 is provided adjacent to the outside of the hermetic container 60, and stores the low-pressure refrigerant flowing from the outside (for example, the evaporator side of the refrigeration cycle) and separates the refrigerant from the accumulator. 61, a suction pipe 62 for introducing the gas refrigerant in the accumulator 61 into the sealed container 60, and a suction port 63 for guiding the gas refrigerant introduced into the sealed container 60 to the suction chamber in the cylinder 11. Yes. Further, the compressor 1 is discharged into a space inside the sealed container 60 and a discharge port (not shown) for discharging the high-pressure gas refrigerant compressed in the compression chamber inside the cylinder 11 into the space inside the sealed container 60. And a discharge pipe 64 for discharging high-pressure gas refrigerant to the outside (for example, the condenser side of the refrigeration cycle).
  • the volume of the suction chamber and the compression chamber in the cylinder 11 is gradually changed by the revolving motion of the rolling piston 15 and the reciprocating motion of the vane 17. Due to the volume change of the suction chamber and the compression chamber, the low pressure gas refrigerant is sucked into the suction chamber via the suction pipe 62 and the suction port 63, and the sucked low pressure gas refrigerant is compressed to high temperature and high pressure in the compression chamber.
  • the compressed high-pressure gas refrigerant is discharged from a discharge valve (not shown) provided in the upper bearing 12 to a space in the sealed container 60 via a discharge muffler chamber.
  • the high-pressure gas refrigerant discharged into the space inside the sealed container 60 is discharged from the discharge pipe 64 to the outside of the sealed container 60.
  • FIG. 4 shows a cross-sectional configuration (a) when the cylinder 11 is relatively thick and a cross-sectional configuration (b) when the cylinder 11 is relatively thin in the general compression mechanism 10.
  • the winding diameter and wire diameter of the vane spring 19 are the same, and the inner diameter of the spring insertion hole 18 into which the vane spring 19 is inserted is also the same. This is because if the winding diameter of the vane spring 19 is reduced, the winding length of the vane spring 19 becomes insufficient, so that the stress generated in the vane spring 19 during expansion and contraction increases and the vane spring 19 breaks. It is because it ends. Further, when the winding diameter of the vane spring 19 is reduced, if the wire diameter of the vane spring 19 is reduced in order to maintain the stress generated in the vane spring 19, a sufficient urging force against the vane 17 cannot be secured. It is.
  • the thickness (axial dimension) of the bridge portion 20 is reduced by the reduction in the thickness of the cylinder 11.
  • the cross-sectional area of the bridge portion 20 decreases.
  • FIG. 5 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment.
  • the vertical direction in FIG. 5 represents the axial direction of the cylinder 11.
  • the spring insertion hole 18 of the present embodiment has an elliptical flat hole shape in at least a part of the spring insertion hole 18 in the axial direction (stretching direction) (the whole in this example). have.
  • the inner diameter of the spring insertion hole 18 in the axial direction of the cylinder 11 is set to a height dimension H11, and the tangential direction of the cylinder 11 in a plane perpendicular to the axial direction of the cylinder 11 (hereinafter simply referred to as “tangential line of the cylinder 11”).
  • the height dimension H11 is smaller than the width dimension W11 (H11 ⁇ W11).
  • FIG. 6 is a diagram showing a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction.
  • the vertical direction in FIG. 6 represents the axial direction of the cylinder 11 with the vane spring 19 inserted into the spring insertion hole 18.
  • the vane spring 19 of the present embodiment has an elliptical flat winding shape in at least a part of the vane spring 19 in the axial direction (in this example, the whole).
  • the vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG.
  • the vane spring 19 is inserted such that the winding diameter (height dimension H21) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W21) in the tangential direction of the cylinder 11 (H21 ⁇ W21). It is inserted into the hole 18.
  • the compressor 1 includes the hollow cylinder 11 housed in the sealed container 60, the rolling piston 15 that rotates eccentrically along the inner peripheral surface 11a of the cylinder 11, A vane 17 that contacts the outer peripheral surface of the rolling piston 15 and divides the space in the cylinder 11 into a suction chamber and a compression chamber; and a vane spring 19 that biases the vane 17 toward the rolling piston 15.
  • a spring insertion hole 18 into which the vane spring 19 is inserted is formed.
  • the spring insertion hole 18 has a height dimension H11 in the axial direction of the cylinder 11 at least in a part of the spring insertion hole 18 in the axial direction.
  • the vane spring 19 has a winding shape in which the height dimension H21 in the axial direction of the cylinder 11 is smaller than the width dimension W21 in the tangential direction of the cylinder 11 in at least a part of the vane spring 19 in the axial direction. It is what you have.
  • the thickness of the cylinder 11 can be reduced while suppressing a reduction in the cross-sectional area of the bridge portion 20.
  • the contact length between the cylinder 11 and the sliding component can be shortened, so that the leakage of refrigerant from the high pressure side space to the low pressure side space of the compression chamber can be reduced.
  • the compressor 1 can be reduced in size in the axial direction, and the material for manufacturing the compressor 1 can be reduced. Further, by reducing the thickness of the cylinder 11, it is possible to increase the number of cylinders without increasing the shell capacity of the compressor 1.
  • the cylinder 11 can be thinned while maintaining the performance of the compressor 1.
  • the vane spring 19 has a flat winding shape, a necessary winding length can be ensured even if the height dimension H21 is reduced. Accordingly, it is possible to maintain the durability of the vane spring 19 while ensuring the urging force of the vane spring 19 against the vane 17.
  • the tension of the end winding part located at the end opposite to the vane 17 is used to remove the vane spring 19. It may be fixed to the spring insertion hole 18.
  • the tension applied by the end winding portion is applied to the entire circumference of the inner peripheral surface of the spring insertion hole 18.
  • the entire vane spring 19 including the end winding portion is flat, the direction of the tension applied by the end winding portion can be limited, and the tension itself applied by the end winding portion can be easily adjusted. . Therefore, since the end winding portion can be made difficult to come off from the spring insertion hole 18, the vane spring 19 can be reliably fixed to the spring insertion hole 18.
  • the spring insertion hole 18 is a deep hole, it has been difficult to process the spring insertion hole 18 into a flat hole shape as in the present embodiment with conventional processing equipment such as a drilling machine. However, in recent years, with the progress of processing equipment and processing technology, it is possible to process the spring insertion hole 18 as in the present embodiment.
  • FIG. 7 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment.
  • symbol is attached
  • the spring insertion hole 18 of the present embodiment has an oval shape (for example, two semicircular arcs) in at least a part of the spring insertion hole 18 in the axial direction (the whole in this example). It has a flat hole shape (rounded rectangular shape defined by two parallel straight lines).
  • the height dimension H12 of the spring insertion hole 18 in the axial direction of the cylinder 11 is smaller than the width dimension W12 of the spring insertion hole 18 in the tangential direction of the cylinder 11 (H12 ⁇ W12).
  • FIG. 8 is a diagram illustrating a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction.
  • the vane spring 19 of the present embodiment has an oblong flat winding shape in at least a part of the vane spring 19 in the axial direction (in this example, the whole).
  • the vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG.
  • the vane spring 19 is inserted such that the winding diameter (height dimension H22) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W22) in the tangential direction of the cylinder 11 (H22 ⁇ W22). It is inserted into the hole 18.
  • the same effect as in the first embodiment can be obtained.
  • the circumference of the ellipse is longer than the circumference of the ellipse. Therefore, in this embodiment, the winding length of the vane spring 19 is made longer than that in the first embodiment. be able to.
  • the outer periphery of the ellipse is configured by a straight line and an arc, the drilling process of the spring insertion hole 18 can be performed more easily than in the first embodiment.
  • FIG. 9 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment.
  • symbol is attached
  • the spring insertion hole 18 of the present embodiment has a rectangular flat hole shape in at least a part of the spring insertion hole 18 in the axial direction (in this example, the whole). Yes.
  • the height dimension H13 of the spring insertion hole 18 in the axial direction of the cylinder 11 is smaller than the width dimension W13 of the spring insertion hole 18 in the tangential direction of the cylinder 11 (H13 ⁇ W13).
  • FIG. 10 is a diagram showing a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction.
  • the vane spring 19 of the present embodiment has a rectangular flat winding shape in at least a part of the vane spring 19 in the axial direction (the whole in the present example).
  • the vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG.
  • the vane spring 19 is inserted such that the winding diameter (height dimension H23) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W23) in the tangential direction of the cylinder 11 (H23 ⁇ W23). It is inserted into the hole 18.
  • the same effect as in the first embodiment can be obtained.
  • the circumference of the rectangle is longer than the circumference of the ellipse and the ellipse. Therefore, in the present embodiment, the winding length of the vane spring 19 is greater than those of the first and second embodiments. The length can be increased. Furthermore, since the outer periphery of the rectangle is configured by a straight line, in this embodiment, the drilling of the spring insertion hole 18 can be performed more easily than in the first embodiment.
  • FIG. 11 is a perspective view showing the configuration of the cylinder 11 of the compressor 1 according to the present embodiment.
  • symbol is attached
  • the spring insertion hole 18 of the present embodiment has a polygonal shape (in this example, a hexagonal shape) in at least a part of the spring insertion hole 18 in the axial direction (in this example, the whole). It has a flat hole shape.
  • the polygon is a shape surrounded by three or more line segments.
  • the height dimension H14 of the spring insertion hole 18 in the axial direction of the cylinder 11 is smaller than the width dimension W14 of the spring insertion hole 18 in the tangential direction of the cylinder 11 (H14 ⁇ W14).
  • FIG. 12 is a diagram showing a configuration in which the vane spring 19 of the compressor 1 according to the present embodiment is viewed in the axial direction.
  • the vane spring 19 of the present embodiment is a flat polygonal shape (in this example, a hexagonal shape) in at least a part of the vane spring 19 in the axial direction (in this example, the whole). It has a winding shape.
  • the vane spring 19 has a winding shape that can be inserted into the spring insertion hole 18 shown in FIG.
  • the vane spring 19 is inserted such that the winding diameter (height dimension H24) in the axial direction of the cylinder 11 is smaller than the winding diameter (width dimension W24) in the tangential direction of the cylinder 11 (H24 ⁇ W24). It is inserted into the hole 18.
  • the same effect as in the first embodiment can be obtained. Further, since the outer periphery of the polygon is formed of a straight line, in this embodiment, the drilling process of the spring insertion hole 18 can be performed more easily than in the first embodiment.
  • the present invention is not limited to the above embodiment, and various modifications can be made.
  • the vertical type compressor is taken as an example, but the present invention is also applicable to a horizontal type compressor.
  • the compressor having one cylinder is taken as an example, but the present invention is also applicable to a compressor having two or more cylinders.
  • the spring insertion hole and the vane spring each having a shape in which the height dimension is smaller than the width dimension in the whole axial direction are described as examples.
  • the spring insertion hole of the present invention may have a hole shape in which the height dimension is smaller than the width dimension only in a part in the axial direction and the height dimension and the width dimension are the same in other parts in the axial direction.
  • the vane spring of the present invention has a winding shape in which the height dimension is smaller than the width dimension only in one part in the axial direction, and the height dimension and the width dimension are equal in other parts in the axial direction, for example. Also good.
  • each of the spring insertion hole and the vane spring may have a shape in which the height dimension is smaller than the width dimension at least in a portion corresponding to the bridge portion (a portion on the outer peripheral side of the vane groove in the radial direction of the cylinder). desirable. According to this, similarly to the above-described embodiment, it is possible to reduce the thickness of the cylinder while suppressing a reduction in the cross-sectional area of the bridge portion.

Landscapes

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

Abstract

Un compresseur (1) comprend : un cylindre (11) ; un piston rotatif (15) qui tourne de manière excentrique le long d'une surface périphérique interne (11a) du cylindre (11) ; une palette (17) qui est en contact avec la surface périphérique externe du piston rotatif (15) et qui divise l'espace à l'intérieur du cylindre (11) en une chambre d'aspiration et une chambre de compression ; et un ressort de palette (19) qui commande la palette (17) de manière qu'elle se dirige du côté piston rotatif (15). Un trou d'insertion de ressort (18) dans lequel le ressort de palette (19) est inséré est formé dans le cylindre (11), la forme du trou d'insertion de ressort (18) est conçue pour que la hauteur H11 dans le sens axial du cylindre (11) soit inférieure à la largeur W11 dans le sens tangentiel du cylindre (11), le ressort de palette (19) est un ressort hélicoïdal et présente une forme de spirale de telle sorte que la hauteur H21 dans le sens axial du cylindre (11) est inférieure à la largeur W21 dans le sens tangentiel du cylindre (11).
PCT/JP2015/062892 2015-04-28 2015-04-28 Compresseur Ceased WO2016174751A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2017515334A JP6388715B2 (ja) 2015-04-28 2015-04-28 圧縮機
PCT/JP2015/062892 WO2016174751A1 (fr) 2015-04-28 2015-04-28 Compresseur
CN201620245576.9U CN205714766U (zh) 2015-04-28 2016-03-28 压缩机
CN201610183692.7A CN106089709A (zh) 2015-04-28 2016-03-28 压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/062892 WO2016174751A1 (fr) 2015-04-28 2015-04-28 Compresseur

Publications (1)

Publication Number Publication Date
WO2016174751A1 true WO2016174751A1 (fr) 2016-11-03

Family

ID=57198271

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/062892 Ceased WO2016174751A1 (fr) 2015-04-28 2015-04-28 Compresseur

Country Status (3)

Country Link
JP (1) JP6388715B2 (fr)
CN (2) CN106089709A (fr)
WO (1) WO2016174751A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111120325A (zh) * 2018-10-31 2020-05-08 广东美芝精密制造有限公司 用于压缩机的泵体组件及旋转式压缩机

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016174751A1 (fr) * 2015-04-28 2016-11-03 三菱電機株式会社 Compresseur
CN108252910B (zh) * 2017-11-30 2024-06-18 刘悦吟 一种压缩机
CN111566351B (zh) * 2018-01-19 2021-12-28 三菱电机株式会社 旋转式压缩机
CZ309169B6 (cs) * 2018-03-23 2022-04-06 Mitsubishi Electric Corporation Hermetický kompresor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56157394U (fr) * 1980-04-25 1981-11-24
JPS58167787U (ja) * 1982-05-06 1983-11-09 松下冷機株式会社 ロ−タリ−式圧縮機
JPS5999189U (ja) * 1982-12-23 1984-07-04 三菱電機株式会社 回転式圧縮機

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101240797A (zh) * 2008-03-07 2008-08-13 广东美芝制冷设备有限公司 一种旋转式压缩机的滑片弹簧及其应用
WO2016174751A1 (fr) * 2015-04-28 2016-11-03 三菱電機株式会社 Compresseur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56157394U (fr) * 1980-04-25 1981-11-24
JPS58167787U (ja) * 1982-05-06 1983-11-09 松下冷機株式会社 ロ−タリ−式圧縮機
JPS5999189U (ja) * 1982-12-23 1984-07-04 三菱電機株式会社 回転式圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111120325A (zh) * 2018-10-31 2020-05-08 广东美芝精密制造有限公司 用于压缩机的泵体组件及旋转式压缩机

Also Published As

Publication number Publication date
CN106089709A (zh) 2016-11-09
CN205714766U (zh) 2016-11-23
JP6388715B2 (ja) 2018-09-12
JPWO2016174751A1 (ja) 2017-11-30

Similar Documents

Publication Publication Date Title
JP6388715B2 (ja) 圧縮機
US9145890B2 (en) Rotary compressor with dual eccentric portion
JP5152385B1 (ja) 圧縮機
CN101737325B (zh) 回转式压缩机
KR101809862B1 (ko) 밀폐형 압축기
CN109153063B (zh) 压缩机、压缩机的制造方法以及扩管器具
CN104819154A (zh) 密闭型压缩机
JP2014109204A (ja) 圧縮機
EP3147508B1 (fr) Compresseur électrique de type étanche
CN106014992A (zh) 旋转式压缩机
JP2012036822A (ja) 圧縮機
JP4172514B2 (ja) 圧縮機
JP2013139725A (ja) 揺動ピストン式圧縮機
US10724525B2 (en) Compression mechanism for a compressor
JP5135779B2 (ja) 圧縮機
JP2014190176A (ja) 回転式圧縮機及び冷凍サイクル装置
US20130064703A1 (en) Scroll compressor
JP6091241B2 (ja) 密閉型圧縮機
JP2016021837A (ja) モータおよび圧縮機
JP2008138591A5 (fr)
JP2008141805A (ja) 圧縮機
WO2018138772A1 (fr) Compresseur de type fermé
JP2008169743A (ja) 圧縮機
JP2019035391A (ja) 圧縮機
JP2018109388A (ja) 回転式圧縮機

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: 15890734

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2017515334

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: 15890734

Country of ref document: EP

Kind code of ref document: A1