JP2598953Y2 - Rotary compressor - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor capable of preventing wear of a rotor and a side block.

[0002]

2. Description of the Related Art As shown in FIGS. 3 and 4, a conventional rotary compressor used in an air conditioner for a vehicle or the like has a cylinder 2 provided in a casing 1 between a front side block 4 and a rear side block 5. It is clamped and fastened by fastening bolts (not shown).

The rotor portion 6 housed in the bore 3 of the cylinder 2 has a rotor 7 and a slide vane 8 and is in contact with an inner peripheral surface 3a of the elliptical bore 3 at a contact point. It is rotatably provided by a shaft 10. Five vane grooves 9 are radially formed in the rotor 7, and slide vanes 8 are slidably provided in the vane grooves 9.

When the rotor 6 is rotated by a drive source (not shown) via the shaft 10, the slide vanes 8 protrude from the vane grooves 9 by centrifugal force or the like, and slide along the inner peripheral surface 3 a of the bore 3. Then, the refrigerant, which is the compressible fluid flowing from the inflow port 11 of the casing 1, flows into the compression chamber C through the suction port 12 opened in the front side block 4. Here, the inlet 12 has an inner end face
Same or radially outward as the radial outer end face of rotor 7
Is established in the side blocks 4 and 5
The compression chamber C is defined by the contact points, the inner peripheral surface 3a of the bore 3, the side blocks 4, 5, the slide vanes 8, or the slide vanes 8.

The volume of the compression chamber C changes with the rotation of the rotor section 6, and the refrigerant sealed therein is compressed. The compressed refrigerant is discharged from a discharge port 13 opened in the cylinder 2 against a discharge valve 14, collides with an oil separator 16 from a communication path 15, and then flows out of an outlet 17 to the outside.

A lubricating oil is guided to the vane 8 by using a pump (not shown) or the pressure of a refrigerant.
Lubrication between the inner wall surface of the bore 3 and the side wall of the vane groove 9 or the inner peripheral surface 3a of the bore 3 is performed. An appropriate back force is applied by the lubricating oil fed so that the vane 8 moves from the vane groove 9 toward the inner peripheral surface 3 a of the bore 3.

In the illustrated example, the lubricating oil O is separated into gas and liquid by the collision of the refrigerant with the oil separator 16.
The lubricating oil O is stored in the lubricating oil storage section 18 formed by the bottom of the casing 1 and the side block 5, and the level of the lubricating oil O is pressurized by the pressure of the refrigerant. Therefore, it is guided through a lubricating oil passage 19 or 20 to a bearing, a mechanical seal or the like (hereinafter referred to as a bearing) 21 or a vane back pressure chamber 22, between the bearing 21 or the slide vane 8 and the vane groove 9, the side block 4. , 5 and the side surfaces of the rotor portion 6 are lubricated.

[0008]

By the way, in the conventional rotary compressor, the lubricating oil guided to the side blocks 4 and 5 and the side surface of the rotor 7 tends to stay near the vane back pressure chamber 22 shown in FIG. For this reason, the side surface of the rotor 7 is formed in a tapered shape, and the lubricating oil remaining in this portion is guided to the outside of the rotor. Further, a step 30 is formed on the end face in consideration of the thermal expansion of the rotor 7.

However, when the side surface of the rotor is formed in a tapered shape and the step portion is formed, the end surface of the rotor becomes sharp, and the thrust movement of the shaft 10 causes the end surface of the rotor 7 and both side blocks 4 and 5 to move. Contact surface pressure increases. As a result, there are problems that the slidability of the rotor is reduced and vibration and noise are significantly increased.
In addition, there is a problem that the rotor and the side plate are worn, and wear powder is scattered in the compressor.

[0010] If the side surface of the rotor is formed flat or the step on the end surface of the rotor is omitted, such a problem can be solved. However, slidability is reduced due to accumulation of lubricating oil and thermal expansion of the rotor. The problem will remain unresolved.

The present invention has been made in view of the above-mentioned problems of the prior art. The present invention eliminates a decrease in slidability due to stagnation of lubricating oil and thermal expansion, while improving wear resistance of a rotor and reducing vibration. And to reduce noise.

[0012]

This invention of the rotary compressor in order to achieve the above object, according to an aspect of includes a cylinder which is closed by both side blocks, and and a side provided in a bore of the cylinder is cut dropped tapered surface haunt a rotor which is, and a vane which is slidably disposed within a vane groove formed in the rotor, the base over <br/> down grooves or label over down with the rotation of the rotor the volume of the compression chamber partitioned by a bore inner peripheral surface and both side blocks及beauty base over emissions of the cylinder is variable with to further the side block
The inner end face of the suction port provided at the outer end of the rotor in the radial direction
Configured to be located on the same or radially outward with the surface
Then , in a rotary compressor configured to compress the fluid to be compressed flowing into the compression chamber from the suction port and discharge the compressed fluid to the outside from the discharge port, the end faces of the rotor facing the both side blocks are cut so as to be curved. In addition, a smooth transition from the curved surface to the tapered surface is provided.

[0013]

According to the present invention, the end faces of the rotor facing both side blocks are curved and cut off, so that even if the rotor expands due to heat, the end faces of the rotor do not contact enough to press the side blocks. The slidability is improved, and the generation of vibration and noise can be prevented. In addition, since the end face of the rotor is curved, even when the rotor moves in the thrust with the shaft and comes into contact with the side block, the contact pressure on the contact surface decreases, which also causes the rotor to have sliding and wear resistance. And vibration and noise can be prevented.

In addition, since the taper surface which reduces the diameter from the curved surface toward the center of the rotor is formed on the side surface of the rotor, the lubricating oil retained near the vane back pressure chamber can be guided to the outside of the rotor. In addition, the slidability and wear resistance between the rotor and the side block are improved.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view taken at right angles to an axis of an embodiment of the present invention, and FIG.
Is a graph showing the relationship between the curved diameter of the rotor end face and the surface pressure. Members common to the members shown in FIGS. 3 to 5 are denoted by the same reference numerals, and description thereof is partially omitted.

In this embodiment shown in FIG. 1, a rotor 7 is fixed to a shaft 10 and provided in a cylinder 2 while being sandwiched between a front side block 4 and a rear side block 5. Slight gaps are respectively provided between the side surface of the rotor 7 and both side blocks 4 and 5 to allow thrust movement (movement in the axial direction) of the shaft 10. Therefore, with the thrust movement of the shaft 10, the side surface of the rotor 7 and both side blocks 4, 5
May rotate while contacting.

In this embodiment, in order to guide the lubricating oil, which tends to stagnate in the vicinity of the vane back pressure chamber 22, to the outside of the rotor 7, the side surface of the rotor 7 is tapered (tapered surface) whose diameter is reduced toward the shaft. 7a).

In this embodiment, the end face of the rotor 7 is formed in a curved shape (curved surface 7b). This configuration provides the following two functions.

The first function is to reduce the contact pressure between the end faces of the rotor 7 and the side blocks 4 and 5 which come into contact with the thrust movement of the shaft 10, and the second is that the rotor 7 is Since the end face of the rotor 7 is formed in a curved shape 7b because the end face of the rotor 7 is thermally expanded by the heat generated from the compressed fluid, the end face of the rotor 7 does not press the side blocks 4 and 5 even when the end face is thermally expanded.

The specific dimensions in the latter case can be determined by the linear expansion coefficient of the base material constituting the rotor 7 and the ambient temperature in the cylinder.

Meanwhile, in the former case, F: Load L: circumference of the contact portion length E _1: Young's modulus of the side block E _2: Young's modulus of the rotor [nu _1: the side blocks Poisson's ratio [nu _2: rotor When Poisson's ratio R: radius of the contact portion, the contact surface pressure P can be expressed by the following equation using the Hertzian stress equation: P = 2W / πZ 1. However, W = F / L... 2 Z = [4WR / π {(1-ν ² ) / E ₁ + (1-ν ² ) / E ₂ }] ^1/2 . , 3 are as follows: R ₁ : Curved diameter of this embodiment R ₀ : Conventional end face (considered as extremely small curved diameter) P ₁ : Surface pressure of this embodiment P ₀ : Conventional surface pressure R ₁ >> R By substituting ₀ , P ₁ << P ₀ can be obtained.

That is, assuming that only the radius of curvature R of the end face of the rotor 7 is a variable, the relationship between the surface pressure P and the radius of curvature R is P = Z · R ^{−1/2 according} to the above equations 1, 2, and 3. This is graphed as shown in FIG.

Therefore, even if the rotor 7 is thermally expanded,
When the bending diameter R is determined based on the linear expansion coefficient of the base material constituting the rotor 7 and the ambient temperature in the cylinder, the decrease in the surface pressure P is simultaneously performed so that the end face of the rotor does not press the side blocks 4 and 5. It is only necessary to study and select a bending radius R that is optimal for both.

Next, the operation will be described. Note that portions common to the conventional compressor will be described with reference to FIGS.

When the rotor unit 6 is rotated via the shaft 10 by a drive source (not shown), the slide vanes 8 protrude from the vane grooves 9 by centrifugal force and an appropriate back force of the refrigerant and the lubricating oil. It slides along the peripheral surface 3a. The refrigerant flowing from the inflow port 11 of the casing 1 is supplied to the suction port 1 opened in the front side block 4.
2 and is introduced into the compression chamber C.

Since the volume of the compression chamber C changes with the rotation of the rotor section 6, the refrigerant sealed therein is compressed, compressed, and then discharged from a discharge port 13 opened in the cylinder 2 through a discharge valve 13. 14 and the communication passage 15
After colliding with the oil separator 16, the outlet 17
From the outside.

In this case, the lubricating oil O stored in the lubricating oil storage portion 18 formed by the bottom portion of the casing 1 and the side block 5 is pressurized by the discharged refrigerant to form the lubricating oil passage 19 or 20. It is led to the bearing 21 or the vane back pressure chamber 22 to lubricate the bearing 21 or the space between the slide vane 8 and the vane groove 9.

In this embodiment, the end face 7b of the rotor 7 facing both side blocks 4 and 5 is curved and cut off.
Even if the rotor 7 expands due to heat, the end face 7b of the rotor 7 does not contact to the extent that the side blocks 4 and 5 are pressed, so that the slidability is improved and the generation of vibration and noise can be prevented.

Further, since the end face 7b of the rotor 7 is curved, even if the rotor 7 moves in the thrust direction with the shaft 10 and comes into contact with the side blocks 4 and 5, the contact pressure P on the contact surface decreases, This also improves the slidability and abrasion resistance of the rotor, and can prevent vibration and noise.

Further, since the tapered surface 7a of which the diameter is reduced from the curved surface 7b toward the center of the rotor 7 is formed on the side surface of the rotor 7, the lubricating oil retained near the vane back pressure chamber 22 is removed. It can be guided to the outside, and the slidability and wear resistance between the rotor 7 and the side blocks 4 and 5 are improved.

The embodiments described above are described to facilitate understanding of the present invention, but not to limit the present invention. Therefore, each element disclosed in the above-described embodiment is intended to include all design changes and equivalents belonging to the technical scope of the present invention.

[0032]

As described above, according to the present invention, the end faces of the rotor facing both side blocks are curved and cut off, and a tapered surface is formed which reduces the diameter from the curved surface toward the center of the rotor. So that the operation of the rotor becomes smooth while eliminating the decrease in slidability due to stagnation of lubricating oil and thermal expansion.
Wear of the rotor or the side block is suppressed, and not only scattering of wear powder but also noise and vibration are greatly reduced.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part showing an embodiment of the present invention.

FIG. 2 is a graph showing a relationship between a curved diameter of a rotor end face and a surface pressure according to the embodiment.

FIG. 3 is a sectional view showing a conventional rotary compressor.

FIG. 4 is a sectional view taken along line AA of FIG.

FIG. 5 is a cross-sectional view showing a structure of a conventional rotor end face.

[Explanation of symbols]

2 ... cylinder, 3 ... bore, 3a
... inner peripheral surface of bore, 4 ... front side block, 5 ... rear side block, 6 ...
Rotor part, 7 ... rotor, 7a
... tapered surface 7b ... curved surface 8 ... vane 9 ... vane groove 9a, 9b ... side wall 17 ... discharge port 19 ... lubricating oil passage 22 ... vane back pressure chamber.

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-53-57514 (JP, A) JP-A-2-52988 (JP, U) JP-B-63-32995 (JP, B2) JP-B-62 15506 (JP, Y2) (58) Field surveyed (Int. Cl. ⁶ , DB name) F04C 18/30-18/352 F04C 2/30-2/352

Claims (1)

(57) [Scope of request for utility model registration] (1) Closed by both side blocks (4, 5)
Cylinder (2) andTheInstalled in bore (3) of cylinder (2)
KereAnd the side surface is cut off to form a tapered surface.Rotor (7)
When,TheSliding self-insertion into the vane groove (9) formed in the rotor (7)
And a vane (8) provided at
With rotationTeGroove (9)RabeHaunt (8)
And the inner peripheral surface (3a) of the bore of the cylinder (2)And bothside
Blocks (4, 5) andBibeCompression chamber divided by
The volume of (C) is variable,Further, the side block (4 ,
The inner end face of the suction port (12) provided in (5) corresponds to the rotor (7).
Located on the same or radially outer side as the radial outer end face
And into the compression chamber (C) from the suction port (12).
Flowed inThe fluid to be compressedCompressDischarge to the outside from the discharge port (17)
In the rotary compressor which is made to emit,
The end faces of the rotor (7) facing the side blocks (4, 5)
Shaved to be curved, and from the curved surfaceTaper
So that it transitions smoothly to the surfaceCharacterized by the fact that
Tari compressor.