EP3318760A1 - Compresseur à palettes - Google Patents

Compresseur à palettes Download PDF

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Publication number
EP3318760A1
EP3318760A1 EP16817893.7A EP16817893A EP3318760A1 EP 3318760 A1 EP3318760 A1 EP 3318760A1 EP 16817893 A EP16817893 A EP 16817893A EP 3318760 A1 EP3318760 A1 EP 3318760A1
Authority
EP
European Patent Office
Prior art keywords
vane
arc surface
end portion
pressure chamber
back pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP16817893.7A
Other languages
German (de)
English (en)
Other versions
EP3318760A4 (fr
Inventor
Yoshio Hirota
Yukio Yoshida
Tomoyasu Takahashi
Jin Osawa
Takaaki Nakamura
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.)
Valeo Japan Co Ltd
Original Assignee
Valeo Japan Co Ltd
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 Valeo Japan Co Ltd filed Critical Valeo Japan Co Ltd
Publication of EP3318760A1 publication Critical patent/EP3318760A1/fr
Publication of EP3318760A4 publication Critical patent/EP3318760A4/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—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
    • F04C18/344—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 inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means

Definitions

  • the present invention relates to a vane compressor suitable for a refrigeration cycle using, for example, a working fluid as a refrigerant, more particularly to the structure of a lower end portion in the forward or backward travel direction of the vane of a vane compressor.
  • a vane compressor includes a cylinder having both ends closed by side blocks or the like, a rotor, rotatably housed in the cylinder, that has a perfect circular cross section, a vane groove formed radially inward from an outer peripheral surface of the rotor, and a vane housed in the vane groove movably forward and backward.
  • the vane compressor has the structure in which the vane is brought into slidable contact with the inner peripheral surface of the cylinder by a centrifugal force caused by the rotation of the rotor or a back pressure from a back pressure chamber provided on the bottom of the vane groove.
  • the bottom of the vane groove of the rotor has an arc-shaped cross section and the lower end portion of the vane is arc-shaped so as to match the shape of the bottom of the vane groove. Accordingly, even when the lower end portion of the vane collides with the bottom of the vane groove, impact sound is reduced because arcs make contact with each other.
  • the vane can reach the bottom of the vane groove until the centers in the arcs coincide.
  • the length of the vane along the vane groove is formed so as not to project from the vane groove even when the vane enters the deepest part of the vane groove. Accordingly, even when the vane moves in the vane groove so as to follow the shape of the inner peripheral surface of the cylinder as the rotor rotates and passes through the radial seal portion on the inner peripheral surface of the cylinder, the vane can enter the cylinder groove without interfering with the bottom of the vane groove.
  • the material of the vane compressor can be formed by, for example, forging as described in PTL 2.
  • the vane groove including the back pressure chamber, a through hole into which a shaft is inserted, and the like are formed in advance.
  • the vane groove of the rotor is polished at high accuracy, but the back pressure chamber provided on the bottom of the vane groove has the shape formed by forging as is. Accordingly, when the vane groove is polished, the position of the vane groove deviates from the position of the back pressure chamber and the center of the vane groove in which the vane slides may deviate from the center of the back pressure chamber.
  • the invention addresses the above problems with an object of providing a vane compressor in which the structure of the lower end side in the forward or backward travel direction of a vane is changed so that the shoulder portion of the lower end portion of the vane has difficulty in overriding the arc surface on the side of the concave arc surface of the back pressure chamber and the rotation of the rotor is thereby prevented from being restricted by the vane protruding from the outer peripheral surface of the rotor.
  • a vane compressor includes a cylinder having both ends closed by side block members, a rotor rotatably provided in the cylinder, a vane groove formed radially inward from an outer peripheral surface of the rotor, and a vane housed in the vane groove movably forward and backward, one end portion of the vane making slidable contact with an inner peripheral surface of the cylinder as the rotor rotates, in which a back pressure chamber having a concave arc surface is formed on a bottom of the vane groove, the other end portion of the vane has a convex arc surface facing the concave arc surface of the vane groove, and voids are generated between the vane and the bottom of the vane groove on both sides in a thickness direction of the vane when the other end portion of the vane makes contact with the bottom of the vane groove.
  • the convex arc surface of the other end portion of the vane has a curvature radius smaller than the concave arc surface on the bottom of the vane groove and the voids are thereby generated on both sides of a contact portion between the other end portion of the vane and the bottom of the vane groove.
  • tangential flat surfaces continued to the convex arc surface are formed on both sides in the thickness direction of the other end portion of the vane.
  • the radius of the convex arc surface of the other end portion of the vane can be reduced as compared with the case in which the entire surface facing the concave arc surface on the bottom of the vane groove is the convex arc surface, contact can be concentrated on the position at which the other end portion of the vane makes contact with the bottom of the vane groove. Accordingly, even when, for example, fine foreign matter enters the back pressure chamber, the foreign matter is sandwiched between the other end portion of the vane and the bottom of the vane groove, thereby preventing the possibility that the vane cannot enter the deep part of the bottom of the vane groove.
  • sliding contact surfaces in slidable contact with the vane groove are formed on both sides in the thickness direction of the vane, chamfering for partially removing the sliding contact surfaces and the convex arc surface is performed between the sliding contact surfaces and the convex arc surface of the other end portion of the vane, and the voids are thereby provided.
  • the shoulder portion of the vane it is possible to shave the shoulder portion of the vane or enlarge voids formed between the other end portion of the vane and the bottom of the vane groove on both sides in the thickness direction of the vane when the other end portion of the vane makes contact with the concave arc surface of the vane groove. Accordingly, when the vane enters the deepest part of the vane groove, the shoulder portion of the other end portion of the vane has more difficulty in overriding the arc surface on the side of the concave arc surface of the back pressure chamber.
  • the width of the sliding surface of the vane is narrowed.
  • the position of the shoulder portion of the vane is prevented from being raised toward the outer peripheral surface of the rotor more than necessary, thereby preventing the width of the sliding surface of the vane from being narrowed.
  • the radius of the convex arc surface of the other end portion of the vane can be reduced as compared with the case in which the entire surface facing the concave arc surface on the bottom of the vane groove is the convex arc surface, contact can be concentrated on the position at which the other end portion of the vane makes contact with the bottom of the vane groove. Accordingly, even when, for example, fine foreign matter enters the back pressure chamber, the foreign matter is sandwiched between the other end portion of the vane and the bottom of the vane groove, thereby preventing the possibility that the vane cannot enter the deep part of the bottom of the vane groove.
  • the fourth aspect of the invention it is possible to shave the shoulder portion of the vane or enlarge voids formed between the lower end portion of the vane and the bottom of the vane groove on both sides in the thickness direction of the vane when the lower end portion of the vane makes contact with the concave arc surface of the back pressure chamber. Accordingly, when the vane enters the deepest part of the vane groove, the shoulder portion of the lower end portion of the vane has more difficulty in overriding the arc surface on the side of the concave arc surface of the back pressure chamber.
  • FIGs. 1 and 2 illustrate an example of a vane compressor used for the refrigeration cycle of, for example, an in-vehicle air conditioner.
  • a vane compressor 1 includes a shaft 3, a rotor 4, fixed to the shaft 3, that rotates as the shaft 3 rotates, and first and second housing members 8 and 9 that define a compression space 18 (described later) together with the rotor 4.
  • the first housing member 8 and the second housing member 9 constitute a housing 2.
  • the first housing member 8 includes a cylinder 8a in which the rotor 4 is housed and a rear side block 8b positioned on the rear side in the shaft direction of the shaft 3 with respect to the cylinder 8a, integrally molded with the cylinder 8a, and closing the rear side of the cylinder 8a.
  • the rotor 4 housed in the cylinder 8a is a cylinder having a perfect circular cross section and a center point P1 of the perfect circle is provided with a through hole 4a to which the shaft 3 can be press-fitted, as illustrated in Fig. 2 .
  • the rotor 4 has two vanes 6 to be inserted into two vane grooves 5 opened in the outer peripheral surface of the rotor 4.
  • any of the vanes 6 includes one end portion having sliding contact surfaces 6a and 6a (described later) in slidable contact with the inner peripheral surface of the vane groove 5 described below on both sides in the thickness direction of the vane 6 and the other end portion having a convex arc surface 611a (described later) and slides on the inner peripheral surface of the cylinder 8a by moving forward or backward from the vane groove 5.
  • the vane groove 5 extends radially inward from the outer peripheral surface of the rotor 4.
  • a back pressure chamber 10 having a concave arc surface 101, which will be described later, is formed on the bottom of the vane groove 5.
  • the vane groove 5 and the back pressure chamber 10 are formed so as to penetrate from front side to the rear side along the shaft direction of the rotor 4.
  • the inner peripheral surface of the cylinder 8a has an inner diameter larger than the outer diameter of the rotor 4 and is formed in a perfect circle about a center point P2.
  • the rotor 4 is housed in the cylinder 8a so that the outer peripheral surface of the rotor 4 and the inner peripheral surface of the cylinder 8a form a fine clearance (radial seal portion P3 at which the cylinder 8a is closest to the rotor 4) at one position in the peripheral direction. Since the rotor 4 about the center point P1 is housed in the cylinder 8a as described above, a compression space 18 is defined between the inner peripheral surface of the cylinder 8a and the outer peripheral surface of the rotor 4. This compression space 18 is partitioned by the two vanes 6 housed in the two vane grooves 5 formed in the rotor 4 into two compression chambers 19 and the volumes of the compression chambers 19 are changed as the rotor 4 rotates.
  • the second housing member 9 is configured by integrating a front side block 9a in contact with the front side end surface of the cylinder 8a with a shell 9b, extending in the shaft direction of the shaft 3 from the front side block 9a, that surrounds the outer peripheral surfaces of the cylinder 8a and the rear side block 8b.
  • the second housing member 9 is coupled to the first housing member 8 via a coupling tool 7 such as a bolt.
  • a pulley 20 to which rotational power is transmitted from the power source (not illustrated) of a vehicle via a belt (not illustrated) is rotatably mounted onto a boss section 9c integrated with the front side block 9a and the rotational power is transmitted from the pulley 20 to the shaft 3 via an electromagnetic clutch 21.
  • the second housing member 9 is provided with an intake port 11 and a discharge port 12 of the working fluid (refrigerant gas) and the intake port 11 communicates with an intake space 14 including a space 14a formed in the second housing member 9 and a concavity 14b formed in the cylinder 8a.
  • the shaft 3 is rotatably supported via plain bearings 23 and 24 that are bearing portions held and formed by the front side block 9a of the second housing member 9 and the rear side block 8b of the first housing member 8.
  • a seal member 13 is present between the shaft 3 and the inner side surface of the second housing member 9 in the part close to the base end of the boss section 9C of the second housing member 9 to prevent the working fluid from leaking externally from the opening of the boss section 9c.
  • the peripheral surface of the cylinder 8a is provided with an intake port 25 communicating with the intake space 14 so as to correspond to the compression space 18 and a discharge port 26 communicating with a discharge space 15. Accordingly, when the cylinder 8a is fitted to the shell 9b, the intake space 14 communicates with the compression chambers 19 via the intake port 25, the discharge space 15 having both ends separated by flange sections 8c and 8d is formed between the outer peripheral surface of the cylinder 8a and the inner side surface of the shell 9b, and the discharge space 15 can communicate with the compression chambers 19 via the discharge port 26.
  • the discharge port 26 is opened or closed by a discharge valve 27 housed in the discharge space 15.
  • the discharge space 15 communicates with an oil separator 16 via a passing hole 28 formed in the flange section 8d.
  • the oil separator 16 communicates with the discharge port 12.
  • the rotational power from the power source (not illustrated) is transmitted to the shaft 3 via the pulley 20 and the electromagnetic clutch 21 and, when the rotor 4 rotates, the working fluid having flowed to the intake space 14 from the intake port 11 is sucked by the compression space 18 via the intake port 25. Since the volumes of the compression chambers 19 partitioned by the vanes 6 in the compression space 18 are changed as the rotor 4 rotates, the working fluid between the vanes 6 is compressed and discharged from the discharge port 26 to the discharge space 15 via the discharge valve 27.
  • the working fluid discharged to the discharge space 15 moves in the peripheral direction along the outer peripheral surface (inner side surface of the shell 9b) of the cylinder 8a and is introduced to the oil separating chamber of the oil separator 16 formed in the rear side block 8b via the passing hole 28 formed in the flange section 8d. After that, oil is separated from the working fluid during rotation in the oil separating chamber of the oil separator 16 and then the working fluid is discharged to an external circuit through the discharge port 12.
  • FIG. 3 illustrates embodiment 1 of the invention
  • Fig. 4 illustrates the other example of embodiment 1 of the invention
  • Figs. 5 and 6 illustrate embodiment 2 of the invention
  • Fig. 7 illustrates embodiment 3 of the invention
  • Fig. 8 illustrates a comparative example to be compared with embodiment 1, the other example of embodiment 1, embodiment 2, and embodiment 3.
  • Embodiment 1, the other example of embodiment 1, embodiment 2, and embodiment 3 will be described while being compared with the comparative example.
  • the vane groove 5 in embodiment 1 extends radially inward from the outer peripheral surface of the rotor 4 as described above and has the inner side surfaces in contact with the sliding contact surfaces 6a and 6a of the vane 6 on both sides in the thickness direction of the vane 6.
  • Fig. 3 (a) illustrates a center line C passing through the center in the thickness direction of the vane 6.
  • the back pressure chamber 10 in embodiment 1 includes two side arc surfaces 101a and 101b and one bottom side arc surface 101c positioned between the two side arc surfaces 101a and 101b.
  • the side arc surface 101a, the bottom side arc surface 101c, and the side arc surface 101b that form the back pressure chamber 10 are disposed along an arc S1 assumed about a center point P5 of the back pressure chamber 10 and constitute the concave arc surface 101 of the back pressure chamber 10.
  • a diameter L1 of the back pressure chamber 10 is larger than a dimension L2 (illustrated in Fig. 3(b) ) of the vane groove 5 in the thickness direction of the vane 6.
  • Reference numeral 103 in Fig. 3 indicates the center in the arc of the arc S1 that forms the concave arc surface 101 of the back pressure chamber 10.
  • the back pressure chamber 10 has the concave arc surface 101
  • reference numeral 103 indicates the center in the arc of the arc S1 that forms the concave arc surface 101 of the back pressure chamber 10
  • the center line C passing through the center in the thickness direction of the vane 6 is illustrated.
  • the vane 6 in embodiment 1 has a lower end portion 61 close to the lower end in the forward or backward travel direction of the vane 6 as the other end portion described above.
  • the lower end portion 61 has the convex arc surface 611a in which an entire contact surface 611 facing a bottom side arc surface 102c of the back pressure chamber 10 is along an arc S2. Accordingly, shoulder portions K1 and K2 of the lower end portion 61 coincide with the start end and the terminal end of the arc S2 about the center point P5.
  • a curvature radius L4 of the arc S2 forming the convex arc surface 611a of the lower end portion 61 is smaller than a curvature radius L3 of the arc S1 forming the concave arc surface 101 of the back pressure chamber 10.
  • Reference numeral 63 in Fig. 3 indicates the center in the arc of the arc S2 forming the convex arc surface 611a of the lower end portion 61.
  • the curvature radius L4 of the arc S2 forming the convex arc surface 611a is substantially half the dimension L2 in the thickness direction of the vane 6.
  • the convex arc surface 611a of the lower end portion 61 is a half peripheral surface and the center point P5 of the arc S2 and the shoulder portions K1 and K2 of the lower end portion 61 are positioned in a single line.
  • a center point P4 of the arc S1 does not deviate from the center point P5 of the arc S2 as illustrated in Fig.
  • the curvature radius L4 of the arc S2 forming the convex arc surface 611a of the lower end portion 61 is the same as the curvature radius L3 of the arc S1 forming the concave arc surface 101 of the back pressure chamber 10. Also in this case, when the position of the vane groove 5 does not deviate from the position of the back pressure chamber 10, the center point P4 of the arc S1 does not deviate from the center point P5 of the arc S2 as illustrated in Fig.
  • the position of the vane groove 5 deviates from the position of the back pressure chamber 10
  • the center line C of the vane groove 5 in the thickness direction of the vane 6 and the center point P5 of the back pressure chamber 10 may deviate by approximately a predetermined dimension X1 along the thickness direction of the vane 6 from a set position, as illustrated in Figs. 3 (b) and 8 (b) .
  • center 63 in the arc of the convex arc surface 611a of the contact surface 611 and the center 103 in the arc of the concave arc surface 101 of the back pressure chamber 10 also deviate by the predetermined dimension X1 along the thickness direction of the vane 6, as illustrated in Figs. 3(b) and 8(b) .
  • the shoulder portions K1 and K2 of the lower end portion 61 override the side arc surfaces 101a and 101b of the back pressure chamber 10 as illustrated in Fig. 8(b) when the vane 6 enters the deepest part of the vane groove 5.
  • a clearance G1 is generated between the center 63 in the arc of the convex arc surface 611a of the lower end portion 61 and the center 103 in the arc of the concave arc surface 101 of the back pressure chamber 10 along the forward or backward travel direction of the vane 6. Since this clearance G1 is large, the upper end portion of the vane 6 projects from the outer peripheral surface of the rotor 4, the vane 6 interferes with the inner peripheral surface of the cylinder 8a, possibly disabling the rotation of the rotor 4.
  • the shoulder portions K1 and K2 of the lower end portion 61 have difficulty in overriding the arc surface on the side arc surfaces 101a and 101b of the back pressure chamber 10 as illustrated in Fig. 3(b) .
  • a clearance G2 is generated along the forward or backward travel direction of the vane 6 between the center 63 of the arc surface of the lower end portion 61 and the center 103 of the arc surface of the concave arc surface 101 of the back pressure chamber 10, as illustrated in Fig. 3(b) .
  • this clearance G2 is small, the upper end portion of the vane 6 does not project from the outer peripheral surface of the rotor 4 in embodiment 1, the vane 6 does not interfere with the inner peripheral surface of the cylinder 8a, thereby preventing the rotation of the rotor 4 from being disabled.
  • Fig. 4 illustrates the other example of embodiment 1 illustrated in Fig. 3 .
  • the other example of embodiment 1 will be described below with reference to Fig. 3 .
  • the same components as in embodiment 1 are given the same reference numerals in principle and descriptions are omitted.
  • the lower end portion 61 of the vane 6 in the other example of embodiment 1 is the same as the lower end portion 61 illustrated in Fig. 3 in that the entire contact surface 611 facing the bottom side arc surface 101c of the back pressure chamber 10 is the convex arc surface 611a along the arc S2.
  • the curvature radius L4 of the arc S2 forming the convex arc surface 611a is larger than substantially the half of the dimension L2 in the thickness direction of the vane 6 and smaller than the curvature radius L3 of the arc S1 forming the concave arc surface 101 of the back pressure chamber 10.
  • the convex arc surface 611a of the lower end portion 61 is smaller than a half peripheral surface and the center point P5 of the arc S2 is disposed closer to the sliding contact surface 6a of the vane 6 than the shoulder portions K1 and K2 of the lower end portion 61.
  • the shoulder portions K1 and K2 of the lower end portion 61 have difficulty in overriding the side arc surfaces 101a and 101b of the back pressure chamber 10 as illustrated in Fig. 4(b) .
  • the clearance G2 in Fig. 4(b) generated because the convex arc surface 611a of the lower end portion 61 is raised along the arc of the concave arc surface 101 of the back pressure chamber 10 is small as in embodiment 1 in Fig.
  • the vane 6 does not project from the outer peripheral surface of the rotor 4 also in the other example of embodiment 1, the vane 6 does not interfere with the inner peripheral surface of the cylinder 8a, thereby preventing the rotation of the rotor 4 from being disabled.
  • FIGs. 5 and 6 illustrate embodiment 2 as described above. Embodiment 2 will be described below with reference to Figs. 5 and 6 . However, the same components as in embodiment 1 and the other example of embodiment 1 are given the same reference numerals in principle and descriptions are omitted.
  • the contact surface 611 includes the convex arc surface 611a and two tangential flat surfaces 611b continued to the convex arc surface 611a.
  • the convex arc surface 611a is formed along an arc S3a of a circle S3, centered at P6, that has a radius L5 smaller than the radius L3 of the arc S1 forming the concave arc surface 101 of the back pressure chamber 10, the arc S3a facing the bottom side arc surface 101c.
  • the tangential flat surfaces 611b are formed so as to make contact with the arc S3a forming the convex arc surface 611a in embodiment 2 and the contact flat surfaces 611b are flat surfaces extending from both ends of the arc S3 toward the shoulder portions K1 and K2 while being inclined toward the sliding contact surfaces 6a of the vane 6.
  • the shape of the lower end portion 61 of the vane 6 in embodiment 2 can also be formed by, for example, providing the flat surfaces 611b on both sides in the thickness direction of the lower end portion 61 at the same angle as the oblique angle of the tangential flat surface of the arc surface (arc S1) passing through a point P7 at which the arc S1 forming the concave arc surface 101 of the back pressure chamber 10 and a virtual line V extending from the inner side surface of the vane groove 5 intersect and by connecting the intersection of the flat surface 611b and the flat surface 611b via the arc S3a of the contact circle S3 having the curvature radius L5 smaller than the curvature radius L3 of the arc S1 forming the concave arc surface of the back pressure chamber 10.
  • the flat surface 611b may be slightly inclined toward the shaft line of the vane groove 5 from the same angle as the oblique angle of the tangential flat surface of the arc surface (arc S1) passing through the point P7, which is not illustrated.
  • Fig. 7 illustrate embodiment 3 as described above. Embodiment 3 will be described below with reference to Fig. 7 . However, the same components as in the embodiments described above are given the same reference numerals in principle and descriptions are omitted.
  • the lower end portion 61 of the vane 6 in embodiment 3 is tapered by partially removing the sliding contact surface 6a and a part of the convex arc surface 611a of the vane 6 and forming the chamfered oblique surface 101c with respect to the convex arc surface 611a (the curvature radius L4 of the arc S2 is the same as the curvature radius L3 of the arc S1 forming the concave arc surface 101 of the back pressure chamber 10) having the entire contact surface 611 facing the bottom side arc surface 101c of the back pressure chamber 10 disposed along the arc S2 about the center point P5.
  • the curvature radius L4 of the arc S2 may be smaller than the curvature radius L3 of the arc S1 forming the concave arc surface 101 of the back pressure chamber 10.
  • the chamfered oblique surface 101c may be formed by partially removing the sliding contact surface 6a of the vane 6 or the convex arc surface 611a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP16817893.7A 2015-06-30 2016-06-28 Compresseur à palettes Withdrawn EP3318760A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015130554 2015-06-30
PCT/JP2016/069083 WO2017002785A1 (fr) 2015-06-30 2016-06-28 Compresseur à palettes

Publications (2)

Publication Number Publication Date
EP3318760A1 true EP3318760A1 (fr) 2018-05-09
EP3318760A4 EP3318760A4 (fr) 2019-02-27

Family

ID=57608765

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16817893.7A Withdrawn EP3318760A4 (fr) 2015-06-30 2016-06-28 Compresseur à palettes

Country Status (3)

Country Link
EP (1) EP3318760A4 (fr)
JP (1) JPWO2017002785A1 (fr)
WO (1) WO2017002785A1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3869231A (en) * 1973-10-03 1975-03-04 Abex Corp Vane type fluid energy translating device
JPH0538379U (ja) * 1991-10-29 1993-05-25 カルソニツク株式会社 ロータリーコンプレツサ
JP3108018B2 (ja) * 1996-07-03 2000-11-13 カルソニックカンセイ株式会社 ロータリコンプレッサ

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JPWO2017002785A1 (ja) 2018-04-12
EP3318760A4 (fr) 2019-02-27
WO2017002785A1 (fr) 2017-01-05

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