JPS63230979A - Vane type compressor - Google Patents

Abstract

PURPOSE:To prevent the occurrence of chattering, by a method wherein the peripheral surface of the cam of a vane compressor is formed with a round part, an increase curve part, increasing a vane protrusion amount, a steady curve part, a decrease curve part, and a round part. CONSTITUTION:A pump housing 4 is formed with a cam ring 5, a front side block 6, and a rear side block 7. A cam peripheral surface 5a is formed with a round part A to seal a gap between the outer peripheral surface of a rotor 8 and the inner peripheral surface of the cam ring 5, an increase curve part B to increase a protrusion amount of a vane, a steady curve part C, a decrease curve part D, and a round part E. This constitution prevents the occurrence of chattering, reduces the occurrence of a fluctuation in torque, and besides provides a high delivery amount.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vane compressor used, for example, as a refrigerant compressor for a vehicle air conditioner.

(Prior art and its problems) Conventionally, a cam ring has a cam peripheral surface on its inner peripheral surface and is closed on both sides with side blocks, a rotor rotatably disposed within the cam ring, and a vane groove of the rotor. A vane type compressor is known which is equipped with a plurality of vanes slidably fitted to the side block, the cam ring, the rotor, and the vane, and which compresses fluid by changing the volume of a compression chamber defined by the side block, cam ring, rotor, and vanes. be.

Conventionally, the curved shape of the cam peripheral surface in such a vane type compressor is simply a curve such as S in"α, as disclosed in Japanese Patent Application Laid-Open No. 60-11601. Near the true circle part of the short diameter part of the circumferential surface (the part that seals between the rotor outer circumferential surface and the cam ring inner circumferential surface), the tip of the vane tends to separate from the cam circumferential surface of the cam ring, causing chattering. This is because the increase in the vane protrusion amount immediately after the perfect circle portion becomes large, and if the increase in the vane protrusion amount is made small, there is a problem in that the discharge amount decreases.

(Object of the Invention) The present invention has been made in view of the above circumstances, and provides a vane that does not cause chattering, has small torque fluctuations, can obtain a large discharge amount, and further reduces 1 mechanical loss torque. The purpose is to provide a mold compressor.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention provides a cam ring having a cam peripheral surface on its inner peripheral surface and closed on both sides with side blocks, and a rotatable cam ring inside the cam ring. A rotor is provided, and a plurality of vanes are slidably fitted into vane grooves of the rotor, and the fluid is pumped by changing the volume of a compression chamber defined by the side block, cam ring, rotor, and vanes. In the vane type compressor, the cam circumferential surface has a first perfect circular portion that seals between the rotor outer circumferential surface and the cam ring inner circumferential surface.

an increasing curve section that is continuous with the first perfect circular section and gradually increases the vane protrusion amount; and a steady curve that is continuous with the increasing curve section and keeps the vane protrusion amount constant. a decreasing curved portion that is provided continuously with the steady curved portion and gradually reduces the amount of vane protrusion; and a decreasing curved portion that is provided continuously with the decreasing curved portion and is connected to the rotor outer circumferential surface and the cam ring inner circumferential surface. and a second perfectly circular portion for sealing the gap.

Each of these parts has a curved shape obtained from a mathematical formula.

(Function) Since the amount of vane protrusion immediately before and after the perfect circle portion is reduced, chattering of the vane does not occur at the short diameter portion. Further, since a true circle portion is formed in the long diameter portion, the discharge amount becomes large even if the rotor diameter is the same.

(Example) Hereinafter, one example of the present invention will be described based on the drawings. 1st
The figure is a partially cutaway side view of the vane type compressor of the present invention, and FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG. 1. In both figures, reference numeral 1 denotes a case, which consists of a circular cylindrical body 2 with one end open, and a front head 3 attached to one end of the cylindrical body 2 so as to close the opening. A pump housing 4 is housed within the case 1. The pump housing 4 consists of a cam ring 5, and a front side block 6 and a rear side block 7 that are attached to both open ends of the cam ring 5 so as to close the open ends. It can be stored rotatably.

The cam ring 5 has a cam circumferential surface 5a on its inner circumferential surface, and a gap chamber 10.10 is defined between the inner circumferential surface of the cam ring 5 and the outer circumferential surface of the circular rotor 8 at a 180° symmetrical position. (multi-room type). The rotor 8 is provided with a plurality (for example, four) of vane grooves 11 extending in the radial direction at equal intervals in the circumferential direction, and vanes 12 can freely move in and out of the vane grooves 11 in the radial direction. It is fitted. Therefore, when the shaft 9 is driven once, the rotor 8 rotates, and the centrifugal force generated by the rotation of the rotor 8 and the back pressure of the lubricating oil acting on the bottom of the vane 111 cause the vane 12 to move outward in the radial direction. It pops out and rotates while slidingly contacting the cam peripheral surface 5a.

Each time each vane 12 passes through the suction port 13 formed in the cam ring 5, fluid is sucked into the cavity 10 through the inlet port 14 provided in the front head 3. The space (compression chamber) 10a inside the void chamber 10 defined by the adjacent vanes 12, cam ring 5, and both side blocks 6.7 changes in volume from the minimum to the maximum during the suction stroke and to the maximum during the compression stroke. The fluid that has been sucked in during the suction stroke and pressurized during the compression stroke is discharged from the discharge port 15 provided in the cam ring 5 by pushing open the discharge valve 16, and this cycle is repeated. Compression of the fluid takes place. When the compressed fluid passes through the lubricating oil separator 17, the lubricating oil mixed in the fluid is separated and the case 1
and a discharge chamber 1 formed between the pump housing 4 and the pump housing 4.
Once discharged into 8, an outlet 1 formed in the cylinder 2
9 to an external circuit (not shown).

Next, the shape of the cam peripheral surface 5a, which is a feature of the present invention, will be explained. Since this embodiment is a multi-chamber type, the suction,
One cycle of compression and discharge is completed in 172 rotations (180 degrees), and two cycles are performed in one rotation of the rotor 8. FIG. 3 shows the vane rotation angle θ between 0 and 180 degrees (172 rotations) using model calculation values showing one embodiment of the present invention.
(degrees) and the vane protrusion amount X (m) in comparison with that of a conventional vane type compressor. It clearly shows the characteristics of That is, the basic shape of the cam peripheral surface 5a is the fourth
As shown in the figure, 1) a first perfect circular part A that seals between the outer circumferential surface of the rotor 8 and the inner circumferential surface of the cam ring 5; 2) a first perfect circular part A that is provided continuously with the first perfect circular part A and from which the vane protrudes; Increasing curve part B3) The increasing curve part B where the amount is gradually increased
A steady curve part C4) is provided continuously with the steady curve part C and keeps the vane protrusion amount constant; a decreasing curve part 5 is provided continuously with the steady curve part C and gradually reduces the vane protrusion amount;
A second portion is provided continuously with the decreasing curved portion and seals between the outer circumferential surface of the rotor 8 and the inner circumferential surface of the cam ring 5.
Perfect circular part E It is a curved shape having the above-mentioned parts A-E, and these parts A-E can be expressed by the following formula. First, the definitions of symbols used in the explanation of the following mathematical formulas will be explained.

Ro: radius H of rotor 8: maximum protrusion amount R(θ) of vane 12: protrusion amount of vane 12+radius θ of rotor 8: rotation angle φ of rotor 8. : Rotor 8 from the reference point (0”) to the first perfect circle portion A
Angle φ1 from the reference point (0°) to the front end in the rotating direction of the rotor 8 in the increasing curve part B φ2: From the reference point (0°) to the front end in the rotating direction of the rotor 8 in the steady curve part C Angle φ: Angle from the reference point (0°) to the front end of the rotating direction of the rotor 8 on the decreasing curve part 1) The formula for the first perfect circular part A is R(θ)=R0 However, o'< θ〈φ.

However, φ. θ≦φ1 3) The formula for the steady curve section C is R(θ)=R00H, where φ, 〈θ〈φ2 However, φ, θ≦φ3 5) The formula for the second perfect circle section E is R (θ)=R0 However, φ2 θ≦180° Furthermore, considering the optimal values of φ and φ2, *, “ra
, -t-to'~20'470'~80' [α,
is the suction closure angle (see Figure 4), and if α1 is too small, the suction fluid cannot be suctioned smoothly and well, so α
1 slope of 60° is good. ] φ2 cape 85' to 95'' (If φ2 is too large, the compression stroke will be performed rapidly.) By forming the cam peripheral surface 5a as described above, the broken line in FIG. As shown by the solid line in the figure, the amount of protrusion of the vane 12 is small in the range of rotation angle θ of about 5° to 67°, and Vane 1 in the range of rotation angle θ from 67″ to 109°
2 has a large protrusion amount, and furthermore, the rotation angle θ of the rotor 8 is 10
The amount of protrusion of the vane 12 in the range of about 9'' to 175@ becomes smaller again. That is, the amount of protrusion of the vane 12 at the short diameter portion of the cam peripheral surface 5a becomes smaller than before. Also.

The acceleration of the vane 12 with respect to the rotation angle θ of the rotor 8 is higher for the cam peripheral surface 5a of the present invention shown by the solid line in FIG. 5 than for the conventional cam peripheral surface shown by the broken line in the same figure.

In particular, the acceleration at the short diameter portion where chattering is likely to occur is smaller than in the past.

In the above embodiment, the present invention is applied to a multi-chamber type in which the cavity chambers 10 are provided at 180-degree symmetrical positions, but the present invention is not limited to this, and can also be applied to a single-chamber type.

(Effects of the Invention) As detailed above, the vane compressor of the present invention has a cam circumferential surface that includes a first true circular portion that seals between the rotor outer circumferential surface and the cam ring inner circumferential surface; an increasing curve part that is provided continuously with the perfect circular part and gradually increases the vane protrusion amount; a steady curve part that is provided continuous with the increasing curve part and keeps the vane protrusion amount constant; a decreasing curved portion that is provided continuously with the steady curved portion and gradually reduces the vane protrusion amount; and a decreasing curved portion that is provided continuously with the decreasing curved portion and seals between the rotor outer circumferential surface and the cam ring inner circumferential surface. Second
Each of these parts has a curved shape obtained by a mathematical formula, such as a perfectly circular part.

Therefore, chattering does not occur, torque fluctuations are small, a large discharge amount can be obtained, and the mechanical loss torque is further reduced.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention; FIG. 1 is a partially cutaway side view of a vane compressor of the present invention, and FIG.
3 is a diagram showing the relationship between the rotor rotation angle and the amount of vane protrusion of the vane type compressor of the present invention in comparison with a conventional vane type compressor, and FIG. 4 is a sectional view taken along the line. FIG. 5 is a diagram showing the shape of the cam peripheral surface in the vane type compressor of the present invention, and compares the relationship between the rotor rotation angle and the acceleration constant of the vane of the vane type compressor of the present invention with that of a conventional vane type compressor. FIG. 5... Cam ring, 5a... Cam circumferential surface, 6... Front side block, 7... Rear side block,
8... Rotor, 11... Vane groove, 12... Vane, A... First perfect circular part, B... Increasing curved part, C...
... Steady curve part, D... Decreasing curve part, E... Second perfect circle part.

Claims (1)

[Claims] 1. A cam ring having a cam peripheral surface on its inner peripheral surface and closed with side blocks on both sides, a rotor rotatably disposed within the cam ring, and a plurality of rotors slidably fitted in vane grooves of the rotor. In the vane type compressor, the cam circumferential surface is in contact with the rotor outer circumferential surface, and the fluid is compressed by a change in the volume of a compression chamber defined by the side block, cam ring, rotor, and vane. a first perfect circular part that seals between the inner circumferential surface of the cam ring; an increasing curved part that is provided continuously with the first perfect circular part and gradually increases the amount of protrusion of the vane; and the increasing curved part a steady curve section that is provided continuously and keeps the vane protrusion amount constant; a decreasing curve section that is provided continuously with the steady curve section and gradually reduces the vane protrusion amount; and the decreasing curve section. A second perfect circular part is provided continuously and seals between the rotor outer circumferential surface and the cam ring inner circumferential surface, and each of these parts has a curved shape obtained by a mathematical formula. vane type compressor. 2. The formula for each part is as follows: (1) The first perfect circle part is R(θ)=R_0 However, 0°<θ<φ_0 (2) The increasing curve part is R(θ)=R_0+Hsin5/2
[90/(φ_1-φ_2)(θ-φ_0)] However, φ
_0<θ≦φ_1 (3) The steady curve part is R(θ)=R_0+H However, φ_1<θ<φ_2 (4) The decreasing curve part is R(θ)=R_0+H−Hsin5
/2[90/(φ_3-φ_2)(θ-φ_2)] However, φ_2<θ≦φ_3 (5) The second perfect circular part is R(θ)=R_0 However, φ_3<θ≦180° A vane type compressor according to claim 1, characterized in that: However, R_0: Rotor radius H: Maximum vane protrusion amount R (θ): Vane protrusion amount + rotor radius θ: Rotor rotation angle φ_0: Rotor rotation from the reference point (0°) to the first perfect circle part Angle φ_1 from the reference point (0°) to the front end in the rotor rotational direction of the increasing curved section φ_2: Angle φ_3 from the reference point (0°) to the front end in the rotor rotational direction of the steady curved section: Angle from the reference point (0°) to the front end of the decreasing curve in the rotor rotation direction