JPS60128986A - Vane rotary compressor - Google Patents

Abstract

PURPOSE:To prevent variation of drive torque in vane compressor by splitting the cylinder chamber into three while representing the cross-section curve of the innercircumferential face of each cylinder on polar coordinates relating to the rotary angle against the center of cylinder. CONSTITUTION:The cross-section curve of the innercircumferential face 1a is represented by R=f(theta) on a polar coordinates relating with the rotary angle theta against the center of cylinder 1. Assuming the diameter of the cylinder innercircumferential face 1a at the approaching section of rotor 17 and cylinder 1 is (r), the number of vane 22 is N, the opening angle of suction hole 13 is Ia, the opening angle of the approaching section is Ib, the number of cylinder chamber is S while the number of cylinder chamber starting from zero is SN. The cross-section curve of cylinder innercircumferential face 1a at the portion of cylinder chamber 20 is shown by formula (1) from the end of the vicinity of suction side to the maximum diameter position of the cylinder innercircumferential face 1a while by formula (2) from the maximum diameter position to the vicinity at the delivery side and by the curve f(theta)=r at the approaching section.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention This invention relates to a vane rotary compressor for a car cooler.

Prior art and its problems This type of vane rotary compressor company has
It is important to form the inner peripheral surface of the cylinder continuously over the entire circumference without bending so that the force applied to the vane tips does not change suddenly when the rotor rotates. In addition, in this type of vane rotary compressor, the shape of the inner peripheral surface of the cylinder in the cylinder chamber is formed so that its maximum radius position is biased toward the suction side, and the compression work in the cylinder chamber is reduced by a large rotation angle of the drive shaft. It is known that if this is done over a period of time, fluctuations in the driving torque can be reduced and vibrations and noise can be reduced. Furthermore, if the shape of the cylinder inner circumferential surface is changed by the amount of deviation of the maximum radius position toward the suction side for each cylinder chamber, the peak position of drive torque fluctuation in the cylinder chamber will shift for each cylinder chamber. It has been found that the overall drive torque fluctuation can be significantly reduced.

However, in this way, the maximum radius position of the cylinder chamber is offset toward the suction side, and the amount of offset is different for each cylinder chamber. It is extremely difficult to form such a material manually, and it is a problem that requires a lot of time to be determined experimentally.

Purpose and Overview The present invention solves the above-mentioned problems and provides a cylinder with a shape in which the maximum radius position of the cylinder chamber portion is offset toward the suction side, and the amount of offset is different for each cylinder chamber. The purpose is to provide a vane rotary compressor in which the peripheral surface can be formed extremely easily.
The cross-sectional curve of the cylinder inner peripheral surface in the cylinder chamber part is
Divide these curves into three parts: from the end of the suction side approach part to the maximum radius position of the cylinder inner circumferential surface, from this maximum radius position to the discharge side approach part, and the approach part, and calculate the rotation angle with respect to the center of the cylinder by dividing these curves into three parts. It is expressed in polar coordinates with respect to θ, and in this case, the curves on the suction side and discharge side from the maximum radial position are expressed as a function regarding the opening angle 1a of the suction hole, and the amount of deviation of the maximum radial position can be changed depending on the value of Ia. It is characterized by the fact that

Embodiments Next, embodiments of the present application will be explained based on the drawings. 1 to 4 show the vane rotary compressor of the present invention, in which a front side plate 2 and a rear side plate 3 are arranged on both sides of a cylindrical cylinder 1, and these cylinders 1 and It is integrated with the side plate 2.3 by four connecting bolts 4. The cylinder 1 and the rear side plate 3 are fitted in a cylindrical casing 5 with one end closed and a plurality of peripheral edges 2a of the front side plate 2 attached to the flange 5a of the casing 5. It is integrally attached with a mounting bolt 6. On the outer periphery of the cylinder 1 above, there is a cylinder 1
A notch recess 7 is formed at a symmetrical position with respect to the center of the cylinder 1, and the notch recess 7 forms a discharge chamber 8 between the cylinder 1 and the casing 5. A plurality of discharge holes 9 are formed to communicate with each other, and a discharge valve 10 and a valve support 11 are provided to open and close these discharge holes 9.
is fixed to the outer periphery of the cylinder l within the cutout recess 7. Further, the cylinder I is formed with a suction passage 12 that penetrates from one end to the other, and suction holes 13 that communicate the suction passage 12 with the inside of the cylinder 1 are formed by grooves at both ends of the cylinder 1, respectively. A high-pressure separation chamber 14 and a suction chamber 15 are formed in the casing 5 and are separated from each other by the fitting of the rear side plate 3 . This high-pressure separation chamber 14 is communicated with the discharge chamber 8 through a hole in the side plate 3, and is also communicated with an external discharge hole 16a of the casing 5. Further, the suction chamber 15 is communicated with the suction passage 12 through a hole in the side plate 3, and is also communicated with an external suction hole 16b of the casing 5. Next, a rotor 17 is installed in the cylinder 1, and a drive shaft 18 formed integrally with the rotor 17 is attached to a side plate 2.
．． 3, so that it is rotatably supported. The outer circumferential surface 17a of the rotor 17 is brought close to the cylinder inner circumferential surface 1a at two approach parts 19, forming two sill chambers 20 between the outer circumferential surface 17a and the cylinder inner circumferential surface 1a. Furthermore, four vane grooves 21 are formed on the outer periphery of the rotor 17 at positions that divide the rotor outer periphery into four equal parts, and vanes 22 are fitted in these vane grooves 21 so as to be slidable in the radial direction of the rotor 17. . As shown in FIG. 4, the cylinder inner circumferential surface 1a of the cylinder 1 has a maximum radius position 23 of the bulging portion in the cylinder chamber 20 portion, which is a right-angled bisect of the line connecting the two approaching portions 19 of the cylinder 1 and the rotor 17. It is formed to be offset by an appropriate amount toward the suction side from the line, and the amount of offset at the maximum radius position 23 is formed to be different for each of the two cylinder chambers 20 parts. Further, the cylinder inner circumferential surface 1a is formed to be gently continuous at the maximum radius position 23 and both end portions of the approach portion 19 without bending. The cylinder inner circumferential surface 1a having the shape described above can be formed as follows.

First, r is the radius of the cylinder inner peripheral surface 1a in the approach section 19, N is the number of vanes 21, Ia is the opening angle of the suction hole 13, Ib is the opening angle of the approach section 19, S is the number of cylinder chambers,
SN is a numerical value corresponding to the number assigned to each cylinder chamber 20 in order from 0, R is the distance from the cylinder center of the cylinder inner circumferential surface 1a S is the distance of the cylinder inner circumferential surface 1a from the cylinder center at the maximum radius position 23 The value obtained by subtracting r from The shape of the cylinder inner circumferential surface 1a can be understood from the cross-sectional curve of the cylinder inner circumferential surface 1a (the cutting line of the cylinder inner circumferential surface 1a that appears when cut along a plane perpendicular to the axis of the rotor 17). This cross-sectional curve can be expressed in polar coordinates with respect to the rotation angle θ with respect to the center of the cylinder 1, and if this is set as R=f(θ), then this f(θ) is r
f(θ)=r as the sum of (1-CO3kθ)/2
+5 (1-CO8kθ)/2.

In this equation, the value of k is its C0 as shown in Figure 5.
It represents the number of times the 8TN curve can be displayed in the range of θ from 0 to 360 degrees, that is, the degree of curvature of the C05IN curve. in general.

In vane rotary compressors, two adjacent
It is preferable that the compression chamber between the vanes 22 assumes its maximum volume at the time when it is removed from the suction hole 13.

Therefore, the maximum radius position 23 of the cylinder chamber 20 is located at the center of the compression chamber when the compression chamber is removed from the suction hole.
, the opening angle 0a from the starting point of the suction hole 13 to the maximum radius position 23 can be expressed as 180/N+Ia. Then, within this opening angle range, C0
Considering that a curve that can display exactly half of the 8IN curve represents the cross-sectional curve R1 from the end of the suction side approach portion 19 to the maximum half-inch rear position 23 on the cylinder inner circumferential surface 1a, the above value of k is 360/ (180/N+I a) However, θ is (3
so/5)XSN-(130/N+I a)X (SN
+1)).

f(θ)=r+5 (1-CO8(360O/(180
/N+ I a) X 2) ) / :”--...(
Next, the cross-sectional curve R2 from the maximum radius position 23 force 1 of the cylinder inner circumferential surface 1a to the discharge side approach portion 19 is calculated from the range of θ from 0 to 360 degrees as shown in FIG. Considering that the curve based on the first equation above and the remaining opening angle after subtracting the opening angle Ib closed by the approach part 19 is a curve that can display exactly half of the C08IN curve, f(θ)=r+1 [1-CO3[360θ
/(360-(180/N+Ia+Ib)X2))]/
It can be expressed as 2. However, this cross-sectional curve R2
is the one following the end of the above cross-sectional curve R1, so R2
There is a phase difference of (180/N+I a) degrees between θ in the equation representing the curve of R1 and θ in the equation representing the curve of R1.
In order to match the phase of the curve equation to the curve equation of R1, R
It is necessary to subtract (180/N+Ia) degrees from θ in the equation representing the curve of No. 2 to set the curve starting position to 0 degrees. Furthermore, since the cross-sectional curve R2 is on the downward side, it is necessary to convert the curve start point to the peak position. The peak position in the equation of the R2 curve above is 1 of the opening angle (360-(180/N+I a+I b)X2) representing one cycle of this curve.
/2, so θ in the equation representing the curve of R2 is (3
It is necessary to add 60-(180/N+Ta+Ib)R2)/2 times. Furthermore, there are multiple cylinder chambers 20, and the rotation angle must be converted to 0 degrees for each cylinder chamber. Therefore, from θ in the equation representing the curve of R2, (3
, 60XSN)/S degrees must be subtracted. Therefore, the cross-sectional curve R2 of the cylinder inner peripheral surface 1a from the maximum radius position 23 to the discharge side approach portion 19 can be expressed by the following formula (where θ is (I a + 180/N)
N+1) ~360X (SN+1)/SI b).

f(θ)=r+5[1-Co5[360X[θ-(1
80/N ten I a)+ (360-2X (180/N
+Ia+Ib))/2 (360XSN)/S)/ (
360-(180/N+I a+I b)R2)] Cococo2... (denoted as the second formula) Next, approach part 1
The cross-sectional direction of the cylinder inner circumferential surface 1a at 9, IttR3, can be expressed by the following equation (where, θl; 13
60X (SN+1)/S-I b ~360X (S
N+1)/S).

f (θ)=r... (denoted as the third equation) As mentioned above, the cross-sectional curve of the cylinder inner circumferential surface 1a is expressed by the first equation and the second equation.
The cross-sectional curves R1, R2, and R3 expressed by the following equations can be expressed as a continuous curve. In the cross-sectional curve of the cylinder inner peripheral surface 1a expressed in this way, the maximum radius position 11=23, the starting end of the approach section 19, and the approach section 1
Each tangent at the end of 9 connects each of these contacts to cylinder 1
Each cross-sectional curve R1, R2 is perpendicular to the line connecting the centers of
, R3 are continued without giving up.

Next, a vane bottom pressure groove 24 and a vane bottom pressure relief groove 25 are formed on the inner surface of the front side plate 2, as shown in FIG. This vane bottom pressure groove 24
is communicated with the high-pressure separation chamber 14 via the outer circumference of the drive shaft 18, a high-pressure introduction hole 26, and a lubricating oil passage 27. This vane bottom pressurizing groove 24 is activated only while the vane groove 21 of the rotor 17 is rotated from a position slightly before the terminal end of the suction side approach part 19 to a substantially central position between the suction side approach part 19 and the maximum radius position W23. It is formed into a fan shape so as to communicate with the bottom of the vane groove 21. The vane bottom pressure groove 24 may be formed so as to communicate with the bottom of the vane groove 21 while the vane groove 21 is rotated from the terminal end of the suction side approach portion 19 to around the maximum radius position 23. The vane bottom pressure relief groove 25 is as follows.

It is composed of an arc-shaped communication groove 25a and a linear relief groove 25b whose one end is communicated with the communication groove 25a. The communication groove 25a is formed so as to communicate with the bottom of the vane groove 21 only while the vane groove 21 is rotated from the maximum radius position 23 to the starting position of the discharge hole 9. . The relief groove 25b is formed so that its other end extends in the radial direction to a position close to the outer peripheral surface of the rotor 17, and when the bottom of the vane groove 21 becomes high pressure, the high pressure gas at the bottom is transferred to the communication groove 25a and the relief groove. It is designed to escape into the cylinder chamber 2O through 25b. The vane bottom pressure groove 24 and the vane bottom pressure relief groove 25 are also formed on the inner surface of the rear side plate 3 symmetrically with those of the front side plate 2. The vane bottom pressurizing groove 24 of the rear side plate 3 is communicated with the high pressure separation chamber 14 via the outer circumference of the drive shaft 18 and the high pressure introduction hole 28 . 29 is a mechanical seal chamber formed in the front side plate 2, and 30 is one end of the mechanical seal chamber 2.
9 and whose other end is open to the inner surface of the side plate 2.

With the above configuration, when forming the cylinder inner circumferential surface 1a, the cross-sectional shape of the cylinder inner circumferential surface 1a can be designed extremely easily by using the first, second, and third equations. be able to.

That is, when it is desired to form a cylinder inner circumferential surface 1a with the number of cylinder chambers S=2 and the number of vanes N=4 as shown in FIG. The expanding cylinder chamber 20 is designated as No. 1, and the opening angle 1aO of the suction hole 13 in this No. 0 cylinder chamber 20 portion is 1aO.
By making the size different from the opening angle Tal of the suction hole 13 in the number cylinder chamber 20 portion, the maximum radius position 23 of the cylinder inner circumferential surface 1a of each cylinder chamber 20 portion is As well as being biased towards the suction side with respect to the right angle bisector, the amount of bias is
It is possible to form a cylinder inner surface 1a that differs from part to part and is continuous smoothly over the entire circumference without bending.

Now, hypothetically, Ib=10 degrees, 1aO=40 degrees, Ial=30
As is clear from the first, second, and third equations, the cross-sectional curve of the cylinder inner circumferential surface 1a in the cylinder chamber 20 portion of number 0 is from the end of the suction side approach portion 19 to the maximum radius position 23. However, f(0)=r+'B (1"C083
6θ/17)/2 curve from the maximum radius position 23 to the discharge side approach part 19 is f(θ)=r+S (1-CO8
The cylinder inner peripheral surface 1a at the approach portion 19 is represented by a curve of f(θ)=r with a curve of 36θ/17)/2. Also 1
The cross-sectional curve of the cylinder inner circumferential surface 1a in the cylinder chamber 20 part is f(θ)=r+5 (1=CO512θ15
)/2 curve from the maximum radius position 23 to the discharge side approach part 1
up to 9 is f(θ)=r+5(1-c0S36(θ-1
70)/19)/2(7) in song a.

The cylinder inner circumferential surface 1a at the approach portion 19 is represented by a curve f(θ)=r. The maximum radius position 23 of the No. 0 cylinder chamber 20 portion on the cylinder inner circumferential surface 1a is at a position 85 degrees from the end of the suction side approach section 19, and is on the suction side from the right angle bisector of the line connecting the approach section 19. It is offset by 5 degrees. The values of the first and second equations at this maximum radius position 23 are both f
(θ=85)=r+5, and the curves of the first and second equations are gently continuous. Furthermore, the maximum radius position 23 of the No. 1 cylinder chamber 20 portion is located 75 degrees from the end of the suction side approach section 19, and is offset by 15 degrees toward the suction side from the right angle bisector of the line connecting the approach section 19. , the cylinder chamber 20 of number 0 above.
The phase is 10 degrees different from that of the other parts. The values of the first and second equations at this maximum radius position 23 are both f(θ=255)
=r+5, and the curves of the first equation and the second equation are gently continuous.

Next, when the vane rotary compressor with the above configuration is operated, the rotor 17 rotates in the direction of the arrow and the vane 2
2 is rotated while sliding it on the cylinder inner peripheral surface 1a. As a result, each vane 22 sucks refrigerant gas from the suction hole 13 into the compression chamber between the vanes 22 in the husband's cylinder chamber 20 portion, and then compresses the refrigerant gas in the compression chamber and discharges it from the discharge hole 9 to the discharge chamber 8. The discharged high-temperature, high-pressure refrigerant gas is sent to the high-pressure separation chamber 14 through the external discharge holes 1 and 5.
and sends it to the condenser. When operated in this way, the internal pressure of each compression chamber acts on the rotor 17 via the vane 22 or directly, but in the vane rotary compressor shown in FIGS. 1 to 4, the number of cylinder chambers S
is 2aI and the number of vanes N is set to 4, which is an integral multiple of the number of cylinder chambers, so the internal pressure of the compression chamber applied to the rotor 17 is point symmetrical with respect to the axis of the drive shaft 18 of the rotor 17. Therefore, the load on the bearing can be reduced, and the noise caused by whirling of the rotor 17 can be reduced. In addition, since the compression chamber repeats suction and compression in each cylinder chamber 20 portion, the driving torques A1 and A2 due to the compression work of the vane 22 in each cylinder chamber 20 portion fluctuate, as shown in FIG.
The fluctuations in the driving torques A1 and A2 in each cylinder chamber 20 overlap to produce a composite driving torque fluctuation. In this case, in the vane rotary compressor having the above configuration, the maximum radius position 23 of the cylinder inner circumferential surface 1a in each cylinder chamber 20 portion is biased toward the suction side.

Since the rotation angle of the drive shaft 18 for compressing the compression chamber is large, the compression chamber can be compressed gently as shown in FIG. It can be made smaller than the conventional compressor shown in FIG. 9, and fluctuations in driving torque can be reduced. Furthermore, since the amount of deviation of the maximum radius position W23 toward the suction side differs for each cylinder chamber 20, the peak positions of the driving torques A1 and A2 in each cylinder chamber 20 portion can be shifted as shown in FIG. As a result, fluctuations in the composite drive torque A can be reduced, vibrations and noise caused by fluctuations in the drive torque can be significantly reduced, and energy loss can be reduced. In addition, the vane 22 is connected to the suction side approach portion 1
When the cylinder chamber is rotated from the 9th position to the 20th position, the pressure applied to the tip of the vane 22 switches from high pressure to low pressure, so the vane 22 tends to cause chattering (dancing phenomenon), but this vane 22 is on the suction side. Since the bottom of the vane groove 21 is in communication with the vane groove pressurizing groove 24 while being moved from just before the end of the approach part 19 to the approximately central position between the end of the approach part 19 and the maximum radius position 23, the vane The high pressure gas in the discharge chamber 8 continues to act on the bottom of the vane 22 through the groove pressure groove 24, thereby reliably preventing chattering of the vane 22. Also, when the vane 22 is rotated from the maximum radius position 23 to the discharge hole 9 position, this vane 23
is forced into the vane groove 21 and the pressure at the bottom of the vane groove 21 becomes abnormally high.
2 rotates from the maximum radius position 23 to the discharge hole 9 position, the bottom of the vane groove 21 is in communication with the vane bottom pressure relief groove 25, so the vane 22 is pushed into the vane groove 21 and the vane groove 21 is When the gas pressure at the bottom increases, the vane groove 2
1 efficiently escapes to the compression chamber in the bottom pressure state in the cylinder chamber 20 through the vane bottom pressure relief groove 25 and the gap between the side plate 2.3 and the rotor 17, and the gas pressure at the bottom of the vane groove 21 is reduced. This prevents the temperature from becoming abnormally high. Therefore, the sliding friction force between the vane 22 and the cylinder inner circumferential surface 1a can be reduced, the drive torque can be reduced, and heat generation can be reduced. Figure 9 shows a conventional vane rotary compressor, with the cylinder inner circumferential surface 1aE
The maximum radius position 23E in each cylinder chamber 20E portion is located on the straight bisector of the line connecting the approaching portions 19E. In addition, in the drawing.

17E is a rotor, 18E is a drive shaft, and 22E is a vane. In such a vane rotary compressor, as shown in FIG. 8, the driving torques AIE in the cylinder chambers 20E all overlap, resulting in extremely large fluctuations in the overall combined driving torque AE. In the above embodiment, since the cross-sectional curve of the cylinder inner circumferential surface is formed by continuously forming the curves expressed by the first, second and third equations, the cylinder inner circumferential surface is curved over the entire circumference. Although it has the advantage that it can be formed into a smooth continuous surface, the present invention is not limited to the above formula, and may be formed with various curves.

Effects As described above, in the present invention, the cross-sectional curve of the inner peripheral surface of the cylinder is expressed in polar coordinates with respect to the rotation angle θ with respect to the center of the cylinder, and R=f(θ), and r is the radius of the inner peripheral surface of the cylinder. , N is the number of vanes, Ia is the opening angle of the suction hole, Ib
When is the opening angle of the approach section, S is the number of cylinder chambers, and SN is a numerical value corresponding to the number assigned to each cylinder chamber in order starting from 0, then the cross-sectional curve of the cylinder inner circumferential surface in the cylinder chamber section is defined as the intake side approach. f (θ)=r+≦[1-CO3[360
θ/ ((180/N+I a)X2)] ]/2,
From the maximum radius position to the discharge side approach part, f(θ) = r + 5
C1-CO5[360(θ-(180/N+Ia)+
(360-2X (180/N+Ia+Ib))/2
(360XSN)/S)/(360(180/N+Ia)
+Ib) The cross-sectional curve of the inner peripheral surface of the cylinder can be expressed by separate functional equations that are continuous without bending at the maximum radius position, so when designing a cylinder, it is possible to A desired cylinder inner circumferential surface having an asymmetric cross-sectional curve can be determined extremely easily and quickly, and design costs can be reduced. In addition, as mentioned above, the suction side and the discharge side from the maximum radius position can be expressed by separate functional expressions that include the opening angle Ia of the suction hole, so when the number of cylinder chambers S is 2 or more, By changing the opening angle Ia of the suction hole, there is an advantage that the cylinder inner circumferential surface can be easily formed so that the peak torque generation position of the cylinder chamber is different for each cylinder chamber.

In addition, as mentioned above, each cross-sectional curve can be expressed by a separate functional equation that is continuous without bending, so even if the inner peripheral surface of the cylinder is asymmetrical with respect to the maximum radius position, it can be expressed at the maximum radius position. This has the effect of preventing bending of the inner peripheral surface of the cylinder and allowing smooth rotation of the vane.

[Brief explanation of drawings]

The drawings show an embodiment of the present application, and FIG. 1 is a longitudinal cross-sectional view;
Figure 2 is a sectional view taken along the ■-■ line in Figure 1, Figure 3 is a partially enlarged view of Figure 2, Figure 4 is a sectional view taken along the IV-TV line, Figures 5 and 6.
The figure is an explanatory diagram explaining the curve of the inner peripheral surface of the cylinder, Fig. 7 is a graph showing the relationship between the rotor rotation angle and drive torque, and Fig. 8
The figure is a graph showing the relationship between rotor rotation angle and drive torque in a conventional compressor, and FIG. 9 is a sectional view showing the conventional compressor. ! ... Cylinder, Ia ... Cylinder inner peripheral surface. 8...Discharge hole, 13...Suction hole, 17...Rotor, 17a...Rotor inner peripheral surface, 19...Approach portion % 2
0... Cylinder chamber, 21... Vane groove, 22.
...Vane, 23... Maximum radius position Patent applicant: Howa Kogyo Co., Ltd. No. 1 BJ 2111 Fig. 3 Fig. 4 Fig. 5 Fig. 6 ρ Fig. 9 Fig. 7 Fig. c

Claims (1)

[Claims] 1. A cylinder, and a rotor rotatably disposed within the cylinder, the outer circumferential surface of which is close to the inner circumferential surface of the cylinder, forming a cylinder chamber between the inner circumferential surface of the cylinder and the inner circumferential surface of the cylinder. and a vane that is slidably mounted in a vane groove formed on the outer periphery of the rotor and whose tip is rotated by contacting the inner periphery of the cylinder. The cross-sectional curve is expressed in polar coordinates with respect to the rotation angle θ with respect to the center of the cylinder, and R=f(
θ), r is the radius of the inner peripheral surface of the cylinder at the approach area between the rotor and cylinder, N is the number of vanes, Ia is the opening angle of the suction hole, rb is the opening angle of the approach area, S is the number of cylinder chambers, and SN is Numbers assigned to each cylinder chamber in order starting from 0. When the numerical value corresponds to 3°, the cross-sectional curve of the cylinder inner circumferential surface in the cylinder chamber portion is defined from the end of the suction side approach part to the maximum radius position of the cylinder inner circumferential surface. is f(θ)=r+5E
l-CO8(360θ/ ((180/N+I a)X
2))] /2, and from the maximum radius position to the discharge side approach part, f(θ) = r+ Cl-CO3[360[θ-5(1
80/N+I a)+ (360-2X (180/N
+Ia+Ib))/2 (360XSN)/S)/ [
360 (180/N ten I a+I b)X2)] co/2
A vane rotary compressor characterized in that the approaching portion is connected by a curve expressed by f(θ)=r. 2. The value of S is 2 or more, the value of N is an integral multiple of the value of S, and I
2. The vane rotary compressor according to claim 1, wherein the value of a is different for each cylinder chamber, and the rotational phases of peak torque generation in each cylinder chamber are shifted from each other.