JP2019082139A - Vane-type compressor - Google Patents

Abstract

To suppress the deterioration of a function of a vane-type compressor by making a vane smoothly slide and move in a vane groove even if a tip of the vane is deformed so as to be hung out to a front side in a rotation direction.SOLUTION: A contact relief slope 24 for avoiding contact with a vane 7 is formed on an opening end 22a side of a vane groove 6 on a front side in a rotation direction. The contact relief slope 24 is decided in a state that a tip face 7a of the vane 7 abuts on a short axis of an elliptical internal peripheral face 11 of a cylinder 3 as a reference, and when assuming a plate thickness of the vane 7 as t, the slope is formed so as to gradually increase a groove width of the vane groove 6 toward the opening end 22a with a position of 0.70 t to 0.83 t toward a bottom part 6a of the vane groove 6 from the tip 7a of the vane 7 regarded as a starting point P1. When assuming a capacity of a chamfered part 41 of a rotor 4 which is generated by the formation of the contact relief slope 24 as Va, and assuming a discharge amount of a vane-type compressor 1 as Vb, an inclination angle θ of the contact relief slope 24 is decided so that Va becomes 1% or smaller than Vb.SELECTED DRAWING: Figure 3

Description

  BACKGROUND OF THE INVENTION Field of the Invention The present invention relates to a vane type compressor used for an automotive air conditioner or the like.

  FIG. 5 shows a vane type compressor 100 conventionally used for an air conditioner for automobiles and the like. This vane type compressor 100 has a cylinder 102 having an internal space 101 having an elliptical cross-sectional shape, and a rotor 103 rotatably accommodated in the internal space 101 of the cylinder 102. In the rotor 103, a plurality of vane grooves 104 are formed at equal intervals along the circumferential direction, and substantially rectangular vanes 105 are accommodated in each of the vane grooves 104 so as to slide. The vane grooves 104 are formed so that the vanes 105 can move in the radial direction of the rotor 103.

In the conventional vane type compressor 100 shown in FIG. 5, when the rotor 103 is rotated in the direction of the arrow R (clockwise direction) by the drive shaft 106, the pressure acting on the bottom portion 104a of the vane groove 104 (discharge And the centrifugal force generated by the rotation of the rotor 103, the vane groove 104 is slid radially outward in the vane groove 104, and the vane positioned on the bottom surface 104a side of the vane groove 104 (vane groove 104) The end of 105 is a rear end surface 105b of the vane 105, and the end of the vane 105 located on the opposite side of the rear end 105b is a tip end surface 105a of the vane 105) is an elliptical inner circumferential surface 102a of the cylinder 102. It comes in sliding contact (see FIG. 6). Then, in FIG. 5, assuming that the intersection point of the X axis and the Y axis coincides with the rotation center C1 of the drive shaft 106 and the rotor 103, the vane 105 can move from the suction chamber 107 to the compression space 108a of the second quadrant. The working fluid (such as refrigerant gas) introduced to the space between the inner circumferential surface 102a and the outer circumferential surface 103a of the rotor 103 is compressed by the compression space 108b in the first quadrant, and the pressurized working fluid is discharged first The working fluid introduced through the port 110 and the first discharge valve 111 and introduced from the suction chamber 107 into the compression space 108c in the fourth quadrant is compressed by the compression space 108d in the third quadrant, and the pressurized working fluid is compressed. It discharges via the 2nd discharge port 112 and the 2nd discharge valve 113 (refer patent document 1).
In FIG. 5, in the internal space 101 in which the cross-sectional shape of the cylinder 102 is elliptical, the short axis coincides with the X axis, and the long axis coincides with the Y axis.

JP, 2016-223315, A

  As shown in FIG. 6, in the conventional vane type compressor 100, the tip end surface 105a of the vane 105 collides with the inner peripheral surface 102a of the cylinder 102 during high speed intermittent operation, and the tip end side of the vane 105 rotates forward (arrow The deformed portion (tip side deformation portion 114) eliminates the gap 115 between the vane 105 and the groove wall surface 104b of the vane groove 104, and the vane 105 smooths the inside of the vane groove 104. It is impossible to slide on the slide, which may cause a problem that the function is degraded.

  Therefore, according to the present invention, even if the tip of the vane is deformed so as to project forward in the rotational direction, the vane can slide smoothly in the vane groove so that the deterioration of the function can be suppressed. The purpose is to provide a machine.

  The vane type compressor 1 according to the present invention includes a cylinder 3 having an internal space 2, a rotor 4 rotatably accommodated in the internal space 2 of the cylinder 3, and a plurality of vane grooves formed in the rotor 4. A vane 7 is accommodated so as to be able to slide in 6 and is in sliding contact with the inner circumferential surface 11 of the cylinder 3 when the rotor 4 is rotating. In the vane type compressor 1 according to the present invention, the open end 22a, 22b side of the vane groove 6 located radially outward of the rotor 4 and the open end on the front side in the rotational direction of the rotor 4 A contact relief slope 24 is formed on the side 22 a to avoid contact with the vane 7. Further, the contact relief slope 24 is in a state where the tip end surface 7 a of the vane 7 abuts on the inner peripheral surface 11 of the cylinder 3 at a position where the rotor 4 is in sliding contact with the inner peripheral surface 11 of the cylinder 3 Where the plate thickness of the vane 7 is t, and the contact portion between the virtual plane 39 orthogonal to the sliding direction of the vane 7 and the tip surface 7a of the vane 7 is the tip 7p of the vane 7 and Then, with the position of 0.70t to 0.83t from the tip 7p of the vane 7 toward the bottom 6a of the vane groove 6 as the starting point P1, the opening end 22a on the radially outer side of the vane groove 6 is The inclination angle of θ is formed so as to gradually increase the groove width of the vane groove 6 toward the end. When the volume of the chamfered portion 41 of the rotor 4 generated by forming the contact relief slope 24 is Va and the discharge amount of the vane compressor 1 is Vb, the inclination angle θ of the contact relief slope 24 is , Va is determined to be 1% or less of Vb (Va ≦ 0.01 · Vb).

  Further, the vane type compressor 1 according to the present invention includes a cylinder 3 having an internal space 2, a rotor 4 rotatably accommodated in the internal space 2 of the cylinder 3, and a plurality of rotors 4 formed in the rotor 4. The vane groove 6 is accommodated so as to be slidably movable, and includes a vane 7 which is in sliding contact with the elliptical inner circumferential surface 11 of the cylinder 3 when the rotor 4 is rotating. In the vane type compressor 1 according to the present invention, the vane 7 is disposed on the front surface 7c which is a side surface on the tip end surface 7a side in contact with the inner peripheral surface 11 of the cylinder A contact relief slope 42 is formed to avoid contact of the groove 6 with the groove wall surface 6b. The contact relief slope 42 has a plate thickness of the vane 7 as t, and a contact portion between an imaginary plane 39 orthogonal to the sliding direction of the vane 7 and the tip surface 7 a of the vane 7 is the tip 7p of the vane 7 Assuming that the end of the vane 7 located on the opposite side of the tip 7p of the vane 7 is the back end 7x of the vane 7, 0 from the tip 7p of the vane 7 toward the back end 7x of the vane 7 With a position of 48t to 0.53t as the starting point P1, the inclination angle of θ is formed so as to gradually reduce the thickness of the vane 7 toward the tip 7p of the vane 7. Then, the inclination angle θ of the contact relief slope 42 is such that the volume of the chamfered portion 44 of the vane 7 generated by forming the contact relief slope 42 is Va ′, and the discharge amount of the vane compressor 1 is Vb Then, it is determined that Va ′ is 1% or less of Vb (Va ′ ≦ 0.01 · Vb).

  In the vane type compressor according to the present invention, even if the tip of the vane is deformed so as to project forward in the rotational direction, the vane can slide smoothly in the vane groove and the function is reduced due to the deformation of the tip of the vane Can be reduced.

It is a longitudinal section of a vane type compressor concerning an embodiment of the present invention. FIG. 2 is a cross-sectional view of the vane type compressor shown by cutting along a line A1-A1 in FIG. 1; It is a figure which shows the engagement state of the vane and vane groove at the time of operation | movement of a vane type compressor, and is a figure which shows the state where the vane was pushed most deeply in the vane groove. It is a figure which shows the modification of a vane, and Fig.4 (a) expands and shows the side surface of a vane, FIG.4 (b) is a figure which shows the relationship of the vane and vane groove which a front end side deformation part produced. is there. It is sectional drawing of the conventional vane type | mold compressor, and is a figure corresponding to FIG. It is a figure which shows the state which the front end side deformation part produced in the vane, and Fig.6 (a) is a partially expanded view of FIG. 5, FIG.6 (b) is an enlarged view of B1 part of Fig.6 (a).

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG.1 and FIG.2 is a figure which shows the vane type compressor 1 which concerns on this embodiment. FIG. 1 is a longitudinal sectional view of the vane type compressor 1. 2 is a cross-sectional view of the vane type compressor 1 shown by cutting along a line A1-A1 in FIG.

  As shown in FIG. 1 and FIG. 2, the vane type compressor 1 according to the present embodiment is rotatably accommodated in a cylinder 3 having an inner space 2 having an elliptical cross section and an inner space 2 of the cylinder 3. The rotor 4, the drive shaft 5 that rotates integrally with the rotor 4, the vane 7 housed so as to slide in the grooves of the plurality of vanes 6 formed in the rotor 4, and the front side of the cylinder 3 It has a front head 8 (a side member on the front side) closing the end face, and a rear head 10 (a side member on the rear side) closing a rear end face of the cylinder 3.

  The cylinder 3 is formed by die casting using an aluminum alloy (e.g., ADC 14) and has an elliptical columnar internal space 2 (through hole). As shown in FIG. 2, in the internal space 2 of the cylinder 3, when the intersection point of the X axis and the Y axis coincides with the rotation center C1 of the drive shaft 5 and the rotor 4, the short axis coincides with the X axis and the long axis Match the Y axis. The cylinder 3 accommodates a working fluid (refrigerant gas or the like) in the compression space 12 between the inner peripheral surface 11 having an elliptical cross section orthogonal to the rotation center C1 of the rotor 4 and the outer peripheral surface 4 a of the rotor 4. It has become. A working fluid flows into a compression space 12 between the inner circumferential surface 11 of the cylinder 3 and the outer circumferential surface 4 a of the rotor 4 from a suction chamber 13 of the front head 8 described later.

  The cylinder 3 is a compression space 12 in the first quadrant and a first discharge port 14 that opens to the compression space 12 near the short axis (X axis), and a compression space 12 in the third quadrant and a short axis (X A second discharge port 15 opened in the compression space 12 near the shaft) is provided. Further, the discharge valve storage chamber 16 is recessed on the outer peripheral side of the cylinder 3, and the discharge valve storage chamber 16 is closed by the cylindrical portion 17 of the front head 8 fitted to the outer peripheral surface 3a. The discharge valve storage chamber 16 is in communication with the compression space 12 via the first discharge port 14 and the second discharge port 15. Then, the first discharge port 14 is closed in the discharge valve storage chamber 16 until the pressure in the compression space 12 becomes equal to or higher than a predetermined pressure, and when the pressure in the compression space 12 becomes equal to or higher than the predetermined pressure, the first discharge port 14 And the second discharge port 15 is closed until the pressure in the compression space 12 becomes equal to or higher than the predetermined pressure, and the pressure in the compression space 12 becomes the predetermined pressure. If it becomes above, the 2nd discharge valve 20 (for example, reed valve) which opens the 2nd discharge port 15 is provided.

  The rotor 4 is formed by die casting using an aluminum alloy (for example, ADC 14), the drive shaft 5 is fitted in the shaft hole 21 formed in the central portion, and a drive source (engine, motor, etc., not shown) It is possible to rotate integrally with the drive shaft 5 that is rotationally driven by the The outer peripheral surface 4 a of the rotor 4 is a cylindrical surface, and a substantially crescent-shaped compression space 12 is generated between the outer peripheral surface 4 a and the elliptical inner peripheral surface 11 of the cylinder 3. In the rotor 4, a plurality of vane grooves 6 are formed at equal intervals along the circumferential direction.

  The vane groove 6 has a tip end surface 7a of the vane 7 (when the end surface of the vane 7 located on the bottom 6a side of the vane groove 6 is a rear end surface 7b, the end surface of the vane 7 located on the opposite side of the rear end surface 7b) The radial movement of the vanes 7 is smoothly guided so as to be in sliding contact with the inner circumferential surface 11 of the third embodiment. Further, the vane groove 6 is on the tip end side of the vane 7 on the side of the opening end 22a, 22b located radially outward of the rotor 4 and on the side of the opening end 22a on the front side in the rotational direction of the rotor 4 (arrow R direction). A contact relief slope 24 is formed to avoid contact with the deformation portion 23. Further, the vane groove 6 is chamfered 25 on the side of the opening end 22 a, 22 b located on the radially outer side of the rotor 4 and on the side of the opening end 22 b on the rear side in the rotational direction of the rotor 4. Further, the lubricating oil in the oil storage chamber 26 is supplied to the bottom 6 a of the vane groove 6 in a pressurized state by the pressure of the discharge gas in the discharge guide path 27. As a result, the vanes 7 accommodated in the vane groove 6 are pressed against the inner peripheral surface 11 of the cylinder 3 by the pressure of the lubricating oil supplied to the bottom 6 a of the vane groove 6 and the centrifugal force acting by the rotation of the rotor 4 Be

  The vane 7 is obtained by applying Ni-P plating to the surface of an aluminum alloy (Al-Si alloy), and is formed in a substantially rectangular shape. The vane 7 is a curved surface having a radius of curvature r such that the tip end surface 7 a can make point contact with the inner peripheral surface 11 of the cylinder 3. Further, the vanes 7 have a rear end face 7b in an arc shape.

  The front head 8 abuts on one end side (front side) of the cylinder 3 and closes the one end side of the compression space 12 between the inner peripheral surface 11 of the cylinder 3 and the outer peripheral surface 4 a of the rotor 4 And the cylinder part 17 fitted in the outer peripheral surface 3a of the cylinder 3 and a part of rear head 10 is integrally formed. The front head 8 is formed with a suction port 32 for suctioning the working fluid via a check valve 31 and a suction chamber 13 (low pressure chamber) communicating with the suction port 32. As shown in FIG. 2, a pair of suction chambers 13 are formed so as to be symmetrical twice around the intersection point (rotation center C1) of the X axis and the Y axis, and the rotation direction of the rotor 4 is the direction of arrow R (right In the case of the rotational direction, the compression space 12a in the second quadrant and the compression space 12c in the fourth quadrant are in communication.

  Rear head 10 abuts on the other end side (rear side) of cylinder 3 and closes the other end side (rear side) of compression space 12 between inner peripheral surface 11 of cylinder 3 and outer peripheral surface 4 a of rotor 4 It is supposed to Further, the rear head 10 communicates with a discharge chamber (high pressure chamber) 35 communicated with the discharge valve storage chamber 16 of the cylinder 3 through a through hole 34 formed in the flange portion 33 of the cylinder 3 and a vane type compressor A discharge port 36 for discharging to the outside of 1 and a discharge guide path 27 for communicating the discharge chamber 35 with the discharge port 36 are formed. A part of the discharge guide path 27 (oil separation chamber 27a), together with the oil separation cylinder 37, constitutes an oil separator 38 for separating lubricating oil mixed in the discharge gas. Further, in the rear head 10, an oil storage chamber 26 communicated with the bottom of the oil separation chamber 27a via the oil discharge hole 40 is formed, and a lubricating oil supply passage communicating the oil storage chamber 26 and the bottom 6a of the vane groove 6 (see FIG. Not shown) is formed. The pressure of the discharge gas in the oil separation chamber 27 a acts on the oil storage chamber 26 via the oil discharge hole 40. Therefore, the pressurized lubricating oil is supplied to the bottom 6 a of the vane groove 6.

  In the vane type compressor 1 according to the present embodiment configured as described above, when the rotor 4 is rotated by the drive shaft 5 in the direction of the arrow R (clockwise direction), the vanes 7 move to the bottom 6 a of the vane groove 6. The vane groove 6 is caused to slide radially outward in the vane groove 6 by the pressure of the acting lubricating oil and the centrifugal force generated by the rotation of the rotor 4, and the tip surface 7 a of the vane 7 It is in sliding contact with the circumferential surface 11. Then, the vane 7 receives the working fluid (such as refrigerant gas) introduced from the suction chamber 13 into the compression space 12 a in the second quadrant (the space between the inner peripheral surface 11 of the cylinder 3 and the outer peripheral surface 4 a of the rotor 4). The working fluid compressed and pressurized in the compression space 12b in the first quadrant is discharged through the first discharge port 14 and the first discharge valve 18, and introduced from the suction chamber 13 into the compression space 12c in the fourth quadrant. The working fluid is compressed in the compression space 12 d of the third quadrant, and the pressurized working fluid is discharged through the second discharge port 15 and the second discharge valve 20.

  FIG. 3 is a view showing an engaged state of the vane 7 and the vane groove 6 at the time of operation of the vane type compressor 1, and at a position where the rotor 4 is in sliding contact with the inner circumferential surface 11 of the cylinder 3, the tip of the vane 7 A state in which the surface 7a is in contact with the inner peripheral surface 11 of the cylinder 3 (in the case of this embodiment, a state in which the tip end surface 7a of the vane 7 is in contact with the short axis of the elliptical inner peripheral surface 11 of the cylinder 3) FIG. At this time, the vanes 7 are pushed into the vane grooves 6 most deeply.

  As shown in FIG. 3, in the vane 7, the tip end surface 7 a repeatedly collides with the inner peripheral surface 11 of the cylinder 3 as a result of the vane type compressor 1 being operated at high speed intermittently. It was in sliding contact with the circumferential surface 11 so that the tip end side was deformed so as to project on the front surface 7c which is the side surface on the front side in the rotational direction of the rotor 4 (arrow R direction). Assuming that the plate thickness dimension of the vane 7 is t mm, the tip side deformation portion 23 of the vane 7 has an extension deformation amount δ of 0.018 t (δ = 0.018 t) mm at the front side in the rotational direction. The amount of extension deformation La from the side to the side of the rear end face 7 b was 0.48 t (La = 0.48 t) mm.

  Therefore, in the vane type compressor 1 according to the present embodiment, the vanes 7 can slide and move smoothly in the vane grooves 6 of the rotor 4 even when the vane type compressor 1 is operated at high speed and intermittently. The vane groove 6 is in contact with the tip end side deformation portion 23 of the vane 7 on the side of the open end 22a, 22b located radially outward of the rotor 4 and on the side of the open end 22a on the forward side of the rotor 4 in the rotational direction. A contact relief slope 24 is formed to avoid.

  The contact relief slope 24 is determined based on a state in which the tip end surface 7a of the vane 7 abuts on the short axis of the elliptical inner peripheral surface 11 of the cylinder 3, and the plate thickness of the vane 7 is t. Assuming that the contact portion between the virtual plane 39 orthogonal to the sliding direction of the vane 7 and the tip surface 7a of the vane 7 is the tip 7p of the vane, the variation of the amount of deformation of the tip side deformation portion 23 of the vane 7 is taken into consideration. With the position of Lb (Lb = 0.70t to 0.83t) mm from the tip 7p toward the bottom 6a of the vane groove 6 (along the sliding direction of the vane 7) as the starting point P1, the radial outside of the vane groove 6 The inclination angle of θ is formed so as to gradually increase the groove width of the vane groove 6 toward the side open end 22a. Then, assuming that the volume of the chamfered portion 41 of the rotor 4 generated by forming the contact relief slope 24 is Va and the discharge amount of the vane type compressor 1 is Vb, the inclination angle θ of the contact relief slope 24 is Va It is determined to be 1% or less of Vb (Va ≦ 0.01 · Vb). In the present embodiment, the inclination angle θ of the contact relief slope 24 is in the range of 14 ° to 19 ° (14 ° ≦ θ ≦ 19 °) so that the contact relief slope 24 does not contact the tip side deformation portion 23 of the vane 7. It has been decided. The contact relief slope 24 is processed with the position of Lc from the opening end 22a of the vane groove 6 toward the bottom 6a of the vane groove 6 as the starting point P1 in consideration of actual groove processing of the vane groove 6. Further, the dimension of Lc is calculated by CAD software or the like on the basis of a state where the vane 7 is pushed to the deepest position of the vane groove 6 by the inner circumferential surface 11 of the cylinder 3. Here, Va is set to 1% or less of Vb because it is possible to minimize the influence of the increase in dead volume due to the formation of the contact relief slope 24 on the performance deterioration of the compressor. . In FIG. 3, the chamfered portion 41 is a triangular portion surrounded by the starting point P1, the opening end 22a, and the intersection point P2 between the contact relief slope 24 and the outer peripheral surface 4a of the rotor 4.

  In the vane type compressor 1 according to the present embodiment having the above-described configuration, even if the tip end side deformation portion 23 is generated such that the tip end surface 7a side of the vane 7 is protruded forward in the rotational direction, the vane 7 is Since the contact between the tip end side deformation portion 23 and the groove wall surface 6b of the vane groove 6 is avoided by the contact escape slope 24, the vane 7 can slide smoothly in the vane groove 6, and It is possible to suppress the deterioration of the function due to the deformation.

(Modification)
FIG. 4 is a view showing a modified example of the vanes 7 of the vane type compressor 1. FIG. 4A is an enlarged view of the side surface of the vane 7. FIG. 4B is a view showing the relationship between the vane 7 and the vane groove 6 in which the tip end side deformation portion 23 is generated.

  As shown in FIG. 4, the vane 7 according to this modification does not contact the groove wall surface 6 b of the vane groove 6 with the portion (tip side deformation portion 23) deformed by the high speed intermittent operation. It formed in the front surface 7c which is the side of the tip side of the vane 7 and the front side in the rotational direction (the + X axis direction side). The amount of deformation (.delta., La in FIG. 3) of the portion (tip side deformation portion 23) where the tip side of the vane 7 is deformed so as to project to the front surface 7c side of the vane 7 by high speed intermittent operation. And the same amount of deformation).

  That is, as shown in FIG. 4, assuming that the end of the vane 7 located on the opposite side of the tip 7 p of the vane 7 is the rear end 7 x of the vane 7, the starting point P 1 is the tip 7 p of the vane 7. (A contact portion between an imaginary plane 39 orthogonal to the sliding direction of the vane 7 (the direction along the Y-axis in FIG. 4A) and the tip surface 7a of the vane 7) Along the direction, it is provided at a position of Ld (Ld = 0.48 t to 0.53 t) mm, and is formed so as to gradually reduce the thickness of the vane 7 from the starting point P1 toward the tip 7p. Then, assuming that the volume of the chamfered portion 44 of the vane 7 generated by forming the contact relief slope 42 is Va ′ and the discharge amount of the vane compressor 1 is Vb, the inclination angle θ of the contact relief slope 42 is Va It is determined that 'is 1% or less of Vb (Va' ≦ 0.01 · Vb). In the present modification, the inclination angle θ of the contact relief slope 24 is in the range of 5 ° to 7 ° (5 ° ≦ θ ≦ so that the tip side deformation portion 23 of the vane 7 does not contact the groove wall surface 6 b of the vane groove 6. 7 °). In the vane type compressor 1 using the vane 7 according to the present modification, it is not necessary to form the contact relief slope 24 in the vane groove 6 of the rotor 4. In FIG. 4, the vane 7 is formed so that the tip end surface 7 a is a smooth surface with a radius of curvature r1 and the vicinity of the tip 7 p is chamfered with a curved surface with a radius of curvature r2 (r2 <r1). Further, in FIG. 4, the chamfered portion 44 is surrounded by the start point P 1, an intersection point P 3 of the extension of the contact relief slope 42 and the imaginary plane 39, and an intersection P 4 of the extension of the front surface 7 c of the vane 7 and the imaginary plane 39. It is a triangular part.

  Moreover, the vane type compressor 1 using the vane 7 which concerns on this modification sets the volume of the space which can not contribute to compression of the working fluid in the compression space 12 to Vx, and the discharge amount of the vane type compressor 1 is Vb. Assuming that Vx is 1% or less of Vb (Vx ≦ 0.01 · Vb), the radially outward opening ends 22a and 22b of the vane groove 6 and the front side in the rotational direction of the rotor 4 Chamfer 43 (C chamfer or R chamfer) may be given to the open end 22a of (refer FIG.4 (b)).

  Even if the vane type compressor 1 using the vane 7 according to the present modification as described above is deformed so that the tip end of the vane 7 protrudes forward in the rotational direction (even if the tip side deformation portion 23 is produced) And, since the contact between the tip end side deformation portion 23 of the vane 7 and the groove wall surface 6b of the vane groove 6 is avoided, the vane 7 can slide smoothly in the vane groove 6 and the deformation of the tip of the vane 7 It is possible to suppress the deterioration of the function.

  Although the inner peripheral surface 3a of the cylinder 3 of the vane type compressor 1 shown in FIG. 2 exemplifies the case where the cross-sectional shape is an elliptical shape, it is not limited thereto, and the cross-sectional shape may be a perfect circle. When the cross-sectional shape of the inner peripheral surface 3a of the cylinder 3 is a true circle, the rotational center of the rotor 4 having a true circular cross-sectional shape is disposed offset from the center of the inner peripheral surface 3a of the cylinder 3 The outer peripheral surface 4a of the rotor 4 and the inner peripheral surface 3a of the cylinder 3 are in contact at one place.

DESCRIPTION OF SYMBOLS 1 vane type compressor 2 internal space 3 cylinder 4 rotor 6 vane groove 6a bottom part 6b groove wall surface 7 vane 7a front end surface 7c front end 7p front end 7x rear end 11 inner circumferential surface 22a open end 22b open end 24 contact relief slope 39 virtual plane 41 Chamfered portion 42 Contact relief slope 44 Chamfered portion P1 Starting point

Claims (4)

A cylinder having an internal space,
A rotor rotatably accommodated in the internal space of the cylinder;
A plurality of vane grooves formed in the rotor so as to be slidably movable, and a vane slidably contacting an inner circumferential surface of the cylinder when the rotor rotates;
In a vane-type compressor provided with
A contact relief slope avoiding contact with the vanes is formed on the open end side of the vane grooves located radially outward of the rotor and on the open end side on the forward side in the rotational direction of the rotor. ,
The contact relief slope is determined based on a state in which the tip end surface of the vane abuts on the inner peripheral surface of the cylinder at a position where the rotor is in sliding contact with the inner peripheral surface of the cylinder. Assuming that the plate thickness of the vane is t, and the contact portion between the imaginary plane orthogonal to the sliding direction of the vane and the tip surface of the vane is the tip of the vane, 0. 0 toward the bottom of the vane groove from the tip of the vane. Starting from the position of 70t to 0.83t, the vane groove is formed at an inclination angle of θ so as to gradually increase the groove width of the vane groove toward the opening end radially outward of the vane groove,
The inclination angle θ of the contact relief slope is 1% of Vb, where Va is the volume of the chamfer of the rotor produced by forming the contact relief slope, and Vb is the discharge amount of the vane compressor. It was determined to be less than or equal to (Va ≦ 0.01 · Vb),
Vane type compressor characterized by that. The inclination angle θ of the contact relief slope is 14 ° to 19 ° (14 ° ≦ θ ≦ 19 °).
The vane type compressor according to claim 1, characterized in that: A cylinder having an internal space,
A rotor rotatably accommodated in the internal space of the cylinder;
A vane slidably accommodated in the plurality of vane grooves formed in the rotor, and in contact with the elliptical inner circumferential surface of the cylinder when the rotor rotates;
In a vane-type compressor provided with
The vane has a contact relief slope which prevents contact with the groove wall surface of the vane groove on the front surface which is the side surface on the front side in the rotational direction of the rotor on the tip end side contacting the inner peripheral surface of the cylinder.
The contact relief slope has a thickness t of the vane, a contact portion between an imaginary plane orthogonal to the sliding direction of the vane and the tip surface of the vane as a tip of the vane, and on the opposite side to the tip of the vane Assuming that the end of the vane located is the rear end of the vane, starting from a position of 0.48 t to 0.53 t from the tip of the vane toward the rear end of the vane, the end of the vane is Formed at an inclination angle of θ so as to gradually reduce the thickness of the vanes towards
Assuming that the volume of the chamfer of the vane generated by forming the contact relief slope is Va ′ and the discharge amount of the vane compressor is Vb, the inclination angle θ of the contact relief slope is Vb. It was determined to be 1% or less (Va ′ ≦ 0.01 · Vb),
Vane type compressor characterized by that. The inclination angle θ of the contact relief slope is 5 ° to 7 ° (5 ° ≦ θ ≦ 7 °).
The vane type compressor according to claim 3, characterized in that:

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