JPS58133493A - Vane type compressor - Google Patents

Abstract

PURPOSE:To improve the sealing performance, by inserting a thin plate between a cylinder and a side block then pressure contacting the thin plate against both side faces of a rotor through the delivery chamber pressure. CONSTITUTION:When the pressure from a delivery chamber is applied through each small hole 7a-8a of side blocks 7, 8 onto thin boards 9, 10, said boards 9, 10 are bent to be pressure contacted against the side faces 1c, 1d of a rotor 1. Consequently the sealing performance between said side faces 1c, 1d and the thin boards 9, 10 is improved to reduce the leakage of refrigerant from the compression chamber 11.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vane compressor, and relates to an improvement in the sealing performance of the rotor side surface of the compressor, which aims to reduce the weight by 4IK.

Vane compressors have the advantage of being compact and are used in car coolers and other cooling devices. However, due to the influence of recent energy saving efforts, weight reduction is also possible! It ended up being destroyed. - The RK vane lid compressor has a compressor body consisting of a cylinder surrounding the axial circumference of a rotor into which vanes are fitted, and side blocks fixed to both sides of this cylinder. The rotor accounts for a significant proportion of the total weight. Therefore, it is easy to assume that these compressor bodies and rotors are made entirely of ram metal (meaning aluminum or an alloy mainly composed of aluminum; the same applies hereinafter) as in other types of compressors. .

However, in a vane compressor, there are many parts that come into contact and cause friction, such as the rotor and vane, the vane and cylinder, and the cylinder and side block. There is a problem that seizure occurs when aluminum-based metal is used for both, and the compression chamber made up of the adjacent vanes, rotor, and compressor body is expanded or contracted to perform compression, so it is particularly difficult to use the rotor and cylinder. The parts that contact in the radial direction, that is, the radial seal part of the rotor, have a very small clearance between them (and must be maintained properly, but only a portion is made of aluminum) in order to have good sealing performance and reduce frictional resistance. When aluminum-based metals are used, the thermal expansion coefficient of aluminum-based metals is significantly higher than that of iron-based metals, so it may become difficult to properly maintain the above clearance due to the effects of heat generated during operation. There is a special problem, and the weight can be reduced by using aluminum-based metal only for the vanes, and using iron-based metal (referring to iron or an alloy mainly composed of iron; hereinafter the same) for the compressor body and the compressor. The current situation is that this is not the case.

Therefore, the present 11tkJ applicant filed a previous patent application (Japanese Patent Application
No. 6-62928 > The HA specification proposes a vane pressure ll1iiiIl that aims to reduce weight. This vane compressor has a vane and a cylinder made of iron-based metal, a cylinder and both side blocks made of aluminum-based metal, and a thin plate made of iron-based metal interposed between the rotor, vanes, and both side blocks, and aluminum K, which eliminates the first problem by avoiding contact between metals in the system;
The second problem is solved by fixing the cylinder and the thin plate to both cylinder blocks so that the radial thermal expansion of the cylinder is approximately equal to that of the rotor, thereby realizing @quantization.

However, even in such conventional vane type compressors, the sealing performance of the rotor side surface was not sufficient, and the improvement in compressed sardine performance was insufficient.

The present invention has been made in view of the above-mentioned points, and an object of the present invention is to improve the sealing performance of the rotor side surface of a vane-type compressor. The inserted rotor and #0-Y axis direction j
In a vane type compressor equipped with a cylinder surrounding one circumference and a side block fixed to both sides of the reed cylinder, a thin plate formed of a ferrous metal member is provided between the cylinder and the side block, respectively. At the same time, each of the side blocks is located within the radius of the rotor and 90° in the counter-rotational direction from the radial seal portion of the rotor.
Small holes are bored at predetermined positions within the area, one opening j11i1 of these small holes is made to communicate with the discharge chamber, and the other opening end is made to face each of the thin plates, so that both feed surfaces of the rotor are exposed by the discharge chamber pressure. The present invention provides a vane type compressor in which the thin plates are brought into pressure contact with each other to improve the sealing performance between the two.

An embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

An embodiment of the present invention is shown in FIGS. 1 to 3, in which a 7-cylindrical rotor 1 is made of aluminum-based metal, and the tip of a steel shaft 2 is firmly connected to the center of the rotor 1. In addition, grooves 3 are formed in the radial direction of the rotor 1 with a phase difference of approximately 90°, and vanes 4 made of iron-based metal are slidably fitted into the grooves 3. A vane 4 is housed within a compressor main body 5, which will be described below.

The compressor main body 5 includes a cylinder 6 that surrounds the rotor 1 in the axial direction, front and rear side blocks 7 and 8 in which both cylinders 60 and 60 are fixed at f14KFM, and both side blocks 7.8 and the cylinder 6. A thin plate clamped and fixed between 9. It is composed of IO.

The cylinder 6 is made of iron-based metal and has, for example, an elliptical inner surface. The tip of the top 74 is configured to slide, and the inside of the compressor main body 5 is divided into a plurality of pressure units.

The side block 7.8 is formed of an aluminum-based metal member, and the shaft 2 is rotatably supported on the front side block 7.

Each of these side blocks 7.8 is located within the radius of the rotor 1 and has a radial seal 1 of this rotor 1.
90 in the counter-rotational direction shown by arrow B from a, lb (Fig. 2)
A small hole 7a at a predetermined position within 1°.

7b, ga, and sb (Fig. 2) are bored, and one end of these small holes 7a, 7b and 8a, 8b faces the thin plate 9 and IOK, and the other end faces the discharge chamber 14 in the head 12 and the shell. It communicates with a discharge chamber 15 within 13. The discharge @14 communicates with the discharge chamber 15 via a passage (not shown). Small holes 7a and 7b in side block 7 and small hole 8a in side block 8.

8b are opposed to each other with the rotor 1 interposed therebetween.

Further, inside these side blocks 7 and 8, one end is within the radius of the rotor 1 and the radial seal portion 1a of the rotor 1.
, lb (Fig. 2) at a predetermined position within 90° in the rotational direction, aligned with the small holes 9a, 9b and 10a, 10b drilled in the thin plates 9 and 1O, and opened at the other end or side block 7 and 8 Ji! 1llllll J surfaces 7C and 8e, and open downward facing channels 7c, 7d, and gc.
, 8d are formed. Each of these passages 7C to 8d drains oil accumulated in the shell 13 through a thin plate 9. IO hole 9m,
9b.

These holes 7C to 8d are not necessarily necessary because the holes 7C to 8d are supplied between the thin plates 9 and 10 and the @ faces 1c and td of the rotor 1 through the thin plates 9 and 10b. The IO small holes 9a-10b are also not necessary.

Thin plate 9. 1O is made of a valve flapper material of ferrous metal, such as Swedish steel, and its thickness is 0.1 to 0. °3
As shown in Figure 3, both side blocks 7
．． Shoulder the shape corresponding to 8. And this thin plate 9,1
0 is the rotor l, vane 4 and both side blocks 7.
It is interposed between 8.

Then, each of these thin plates 9 and 10 and the side surface 1c of the rotor 1
, ld are opposed to each other at a predetermined distance d, as shown in the enlarged view of FIG. Incidentally, this interval d is approximately 0.01 to 0.0
It is set to about 5 yen, and the conventional Seki III (d'-0
,01~0.03) is larger than K.

The compressor body 5 is surrounded by a head 12 on the front side and a shell 13 on the rear side.
A suction chamber 17 and a discharge chamber 15 are appropriately partitioned by the head 12 and the shell 13 to form a shape IR'i! It is. The suction chamber 17 is connected to a suction joint 18 having a suction valve (not shown), and communicates with the compression chamber 11 therein. On the other hand, the discharge chamber 15 is connected to a discharge joint 20 fixed to the shell 13 and is communicated with the compression chamber 11 via a discharge hole 21 formed in the cylinder 6, and the outlet of this discharge hole 21 is connected to a discharge joint 20 fixed to the shell 13. It is closed by valve 22.

In the above configuration, when the rotor 1 rotates with the rotation of the shaft 2, the tip of the vane 4 moves to the inner surface K of the cylinder 6.
G rotates while sliding, and the compression chamber 11 between adjacent vanes 4 expands or moves to perform a compression action, and the discharge chamber 1
High pressure refrigerant is discharged into the tank. When this discharge chamber pressure is applied to the thin plates 9 and 10 through the small holes 7a to 8b of the side block 7.8, these thin plates 9 and 10 are bent and deformed as shown in an enlarged view in FIG. and the sides lc, l of rotor 1
d. As a result, both sides 1c and l of the rotor 1
The sealing performance between d and the thin plates 9 and 10 is improved, and leakage of compressed refrigerant from the compression chambers 1'l and 11 is extremely reduced. As a result, compression performance is improved.

In addition, the thin plates 9, 10- that can be pressed into contact with each other and the side surface lc of the rotor l,
There are small holes 7C to 8d in the side block 7.8 between the
Oil is supplied through the small holes 9a to 10b of the thin plates 9 and 10 or from the compression chambers 11 and 111&ll. On the other hand, the page 74, the cylinder 6, and the thin plates 9 and 10 are made of iron-based metal,
Since the rotor 1 and both side blocks 7.8 are made of aluminum-based metal, the contact portions quickly become accustomed to each other, and therefore, the supply of lubricating oil can sufficiently prevent seizure between them.

As explained above, according to the present invention, a thin plate formed of a ferrous metal member is inserted between the cylinder and the side block, and the side block is provided with a radial seal portion of the rotor that is located within the radius of the rotor. 9d in the counter-rotational direction from
The thin plates are communicated with the discharge chamber through a small hole provided at a predetermined position within 100 mm, and the thin plates are brought into pressure contact with both sides of the rotor by the pressure in the discharge chamber, thereby improving the sealing performance between the two. With this, compression performance can be improved. Moreover, since the thin plate is inserted, the performance of the compressor can be improved at low cost. Another advantage is that by selecting the thickness of the thin plate to an appropriate value, the surface pressure with the rotor can be optimized, and the oiliness is not impaired.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing an embodiment of a vane compressor according to the present invention, FIG. 2 is a sectional view taken along the arrow @A-A in FIG. 1, and FIG. FIG. 4 is an enlarged view of the main part of FIG. 1, and FIG. 5 is an explanatory diagram of the operation of FIG. 4. 1...Rotor, 4...Bay16...Cylinder,
7゜8...Side block, 9.10...Thin plate, 1
2...Head, 13...Shell, 18...Suction joint, 20...Discharge valve. Applicant: Agent for Diesel Kiki Co., Ltd. Patent attorney: Toshihiko Watanabe 1st decoy A Procedural amendment (self 1) Commissioner of the Japan Patent Office Kazuo Wakasugi 1, Indication of case Patent Application No. 16060 of 1988 2, Jl Akira Name of Vane Type Compressor 3, Relationship to the case of the person making the amendment Patent applicant address 3-6-7 Shibuya, Shibuya-ku, Tokyo Name (33
3) Diesel Kiki Co., Ltd. Representative: Mochizuki-Sei 4, Agent address: 301 Sunshine Koken Plaza, No. 5, 3-2-4 Higashiikebukuro, Toshima-ku, Tokyo, subject to amendment. (3) On the 7th line of the same page, replace "cylinder block" with "
Corrected to "side block". (4) On page 6, line 13, "compressor" is corrected to "compression chamber."

Claims (1)

[Claims] 1. A vane compressor equipped with a rotor into which vanes are fitted in the middle diameter direction, a cylinder surrounding the scissor rotor in the axial direction, and side blocks fixed to both sides of the cylinder. inserting a glued thin plate made of an iron-based metal member in relation to the side block;
A small hole is formed in each of the side blocks at a predetermined position within the radius of the rotor and within the counter rotational direction Kef from the left side of the radial sea of the rotor, and one open end of each of these small holes is provided. communicates with a discharge chamber, the other open end faces each of the thin plates, and the discharge chamber pressure presses each of the thin plates against both sides of the rotor to improve sealing between the two. vane type compressor.