JP2815527B2 - Scroll 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 scroll type compressor, and more particularly to a scroll type compressor used for a cooling device for an automobile.

[0002]

2. Description of the Related Art Conventionally, a scroll compressor having a pair of scroll members facing each other has been proposed. As shown in FIG. 8, this type of scroll compressor has
A fixed scroll member 60 in which a spiral body 65 is formed on one surface of a plate body fixed in a housing 50 constituting an outer shell, and a spiral body 72 which meshes with the spiral body 65 of the fixed scroll member 60 at a shifted angle. Is formed on one surface of another plate body, and has a movable scroll member 70 that makes a circular orbital movement with respect to the fixed scroll member 60 by a drive mechanism having a rotation shaft 53. In the housing 50, a rotation preventing mechanism 80 having a ball coupling is provided to prevent the movable scroll member 70 from rotating. In the housing, a crank chamber 95 that houses the drive mechanism is formed.

The driving mechanism is a large-diameter portion 5 at one end of the rotating shaft 53.
The eccentric pin 54 at the eccentric position 3b and the eccentric pin 5
The eccentric bush 58 is larger than 4 and has an eccentric pin 54 at an eccentric position, and a boss 73 for accommodating the eccentric bush 58 via a radial bearing 74.

In this compressor, refrigerant gas sucked from a suction port 91 moves from a suction chamber 92 to the center of a pair of spiral bodies according to a circular orbital movement of a movable scroll member 70 with respect to a fixed scroll member 60. The compressed scroll member 60 is compressed and discharged from a discharge port 63 provided at the center of the plate of the fixed scroll member 60 to a discharge chamber 67.
It is discharged from 3.

FIG. 9 shows a centrifugal pump mechanism for lubricating a similar scroll type compressor described in Japanese Utility Model Laid-Open No. 4-91294. This centrifugal pump 100
Is a suction port 101 penetrating through both end faces of the eccentric bush 58.
The centrifugal pump 100 is constituted by the radial bearing 74 and the discharge port 102 of the counterbalance weight 56 communicating with the suction port 101, and a dead-path chamber formed by the eccentric bush 58 and the radial bearing 74 reduces the negative pressure. As a result, the lubricating oil stored in the crank chamber 95 (see FIG. 1) is sucked into the blind lane chamber through a part of the radial bearing 74, and the lubricating oil causes a portion between the eccentric bush 58 and the boss 73, that is, , For lubricating the radial bearing 74.

[0006]

However, in the conventional scroll type compressor described above, the crank chamber 9
5 is sucked by the negative pressure of the blind alley chamber by the negative pressure, and the lubricating oil in the middle is used to lubricate the radial bearing 4. is there. This results in a portion of the radial bearing 74 where no lubricating oil is supplied, thus resulting in poor lubrication and noise and wear.

Therefore, a technical problem of the present invention is to supply a good lubricating oil to a portion between an eccentric bush and a boss portion, to improve the lubricity of this portion, to improve the durability and to provide a scroll having a long life. It is to provide a type compressor.

[0008]

According to the present invention, there is provided a rotary shaft, an eccentric bush eccentric from the rotary shaft and coupled to one end of the rotary shaft, and a boss for rotatably receiving the eccentric bush. A scroll type having a first spiral body having a circular orbital motion in accordance with the rotation of the rotating shaft and a second spiral body meshing with the first spiral body, and obtaining a compressing action of refrigerant gas containing lubricating oil. In the compressor, the eccentric bush has a through-hole extending between both end faces in the axial direction, and the through-hole has an opening at one end face opposed to the boss portion, the opening of which at the other end faces the axis of the rotating shaft. It is inclined away from the center, and is located rearward in the rotation circumferential direction of the rotating shaft with respect to the opening of the one end face facing the boss portion, so that when the rotating shaft rotates, To draw the flow of the refrigerant gas Scroll compressor, characterized in that the straining thus obtained.

According to the present invention, in the scroll compressor, the eccentric bush is formed with a projection for taking in refrigerant gas around the opening at the other end surface of the through hole. A scroll type compressor characterized by the following is obtained.

[0010] According to the present invention, in the scroll compressor, the eccentric bush is formed with a cutout for taking in refrigerant gas around the opening at the other end surface of the through hole. As a result, a scroll type compressor is obtained.

[0011]

According to the present invention, the lubricating oil contained in the refrigerant gas is pressure-fed into the boss by the flow of the refrigerant gas in the through-hole, and passes through the gap around the eccentric bush. Is discharged from At this time, since the refrigerant gas passes through the entire gap around the eccentric bush, lubricating oil is uniformly supplied around the eccentric bush.

[0012]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a sectional view showing the overall structure of a scroll compressor according to a first embodiment of the present invention. As shown in FIG. 1, the housing 50 includes a rear housing 51 formed of a large-diameter cylindrical body with a bottom, and an annular front housing 52 fixed to an open end of the rear housing 51.

A rotating shaft 53 disposed in the housing 50
Has a small diameter portion 53a surrounded by a boss portion 52a of the front housing 52, a large diameter portion 53b surrounded by an end plate portion 52b, and a flange portion 52c.
An eccentric pin 54 extending parallel to the axis X is eccentrically fixed to the end face of the large diameter portion 53b in the radial direction from the axis. The large diameter portion 53 b of the rotating shaft 53 is rotatably supported by the front housing 52 via a radial ball bearing 55.

In the rear housing 51, a fixed scroll member 60 is provided. Fixed scroll member 60
Is a disk-shaped plate 61 fitted to the rear housing 51.
And a leg 62 formed on one side surface of the plate body 61. A discharge hole 63 is formed in the center of the plate 61. A spiral body 65 is formed on the other side surface of the plate. The fixed scroll member 60 is fixed to the rear housing 51 by bolts 64 with the legs 62 in contact with the bottom 51a of the rear housing 51.
The internal space of the rear housing 51 is partitioned into a suction chamber 66 and a discharge chamber 67 by the plate body 61 of the fixed scroll member. In the rear housing 51, a movable scroll member 70 is disposed adjacent to the fixed scroll member 60. The movable scroll member 70 includes a disk-shaped plate 71.
A spiral body 72 formed on one side surface of the plate body 71;
An annular boss 73 is formed on the other side surface of the plate 71. Scroll 72 of movable scroll member 70
Are the spiral body 65 of the fixed scroll member 60 and 180
They are engaged with an angle deviation of °. An eccentric bush 1 having an eccentric pin 54 rotatably at an eccentric position is rotatably accommodated in the boss 73 via a radial bearing 74.

Next, the rotation preventing mechanism of the movable scroll member will be described. The rotation preventing mechanism includes an annular first race 81 provided on the movable scroll member 70 side, a plate-shaped first ring 82 having a plurality of circular holes 82a, and a flange portion facing the movable scroll member 70. An annular second race 83 provided on the inner surface of the second ring 52c and a plurality of circular holes 84 of the same number corresponding to the circular holes 82a of the first ring 82.
a plate-shaped second ring 84 having a
a and a ball member 85 inserted into 84a. The circular holes 82a of the first ring 82 are formed at predetermined intervals in the circumferential direction. Further, the circular holes 84a of the second ring 84 have the same diameter, the same pitch, and the same pitch circle as the circular holes 82a at predetermined intervals in the circumferential direction.

A slight gap is formed between the first ring 82 and the second ring 84. First Race 8
1 and the second race 83, and the circular hole 82 a of the first ring 82 and the circular hole 8 of the second ring 84
4a, the same number of ball members 85 as the circular holes 82a are arranged between the first race 81 and the second race 83.

This compressor is a drive mechanism, and is an eccentric bush 1 eccentric from a rotary shaft and driven by an eccentric pin 54 provided at one end of the rotary shaft, and a radial bearing 74 rotatably supporting the eccentric bush 1. And The rotation of the rotating shaft causes the orbiting scroll member to make a circular orbital motion.

FIG. 2A is a front view showing an eccentric bush of the drive mechanism of the scroll compressor shown in FIG. 1, and FIG.
FIG. 3A is a sectional view taken along line AA of FIG. FIG. 2 (a) and (b)
As shown in the figure, the eccentric bush 1 is eccentric from the center of the rotating shaft by a predetermined distance t, and extends between both end surfaces and penetrates obliquely in a direction intersecting a predetermined angle α with the axial direction. It has a hole 2. The opening at one end of the through hole 2 facing the boss 73 (see FIG. 1) is inclined so as to be further away from the axis of the rotating shaft than the opening at the other end, and the one end face facing the boss. Is located rearward of the opening on the other end surface in the rotational circumferential direction of the rotating shaft. Due to the rotation of the eccentric bush 1, the refrigerant gas introduced into the obliquely provided through hole 2 of the eccentric bush 1 is further radially outward due to the centrifugal force generated by the rotation of the eccentric bush 1, that is, in FIG. The eccentric bush 1 moves in the direction indicated by the arrow 3 and is pressure-fed to the boss portion, and when the boss portion comes out of the boss portion, lubricating oil is satisfactorily supplied to the gap around the eccentric bush 1 to lubricate them. Note that reference numeral 5 in the figure is
An insertion hole for inserting the eccentric pin 54 (see FIG. 1).
2 (b) (outside hatched portions are grooves for engaging with bearings).

FIG. 3 is a front view showing a modified example of the eccentric bush of the drive mechanism of the scroll compressor shown in FIG. A in FIG.
A cross-sectional view taken along the line -A is the same as that shown in FIG. 2B, and is not shown here. Also, FIG.
The same reference numerals are used for portions corresponding to. The opening of the through hole 2 on one end face of the eccentric bush 1 that faces the boss 73 (see FIG. 1) is inclined away from the axis of the rotation shaft more than the opening on the other end, and faces the boss. The opening of the one end face is provided so as to be located outside the center of the eccentric bush 1.

Therefore, the moving speed of the refrigerant gas in the through hole 2 is higher than that in the case of FIG. 2A, but the same effect as in FIG. 2A is obtained.

FIG. 4A is a view showing an eccentric bush 11 according to a second embodiment of the present invention, and FIG. 4B is a sectional view taken along line BB of FIG. 4A. The difference from the first embodiment is that a projection 13 is provided on the other side of the through hole 12 at an acute angle with the end face of the opening 12a. The protrusion 13 makes it easier for the refrigerant gas to be taken in than the eccentric bush according to the first embodiment.
It moves as indicated by arrow 14 in the figure. Reference numeral 15 in the drawing denotes an insertion hole for the eccentric pin.

FIG. 5 is a view showing a modification of the eccentric bush 11 of FIG. FIG. 4 is a sectional view taken along the line BB in FIG.
Since it is the same as that shown in (b), illustration is omitted here. Parts corresponding to FIG. 4 are denoted by the same reference numerals. The opening of the through hole 12 on one end face of the eccentric bush 11 that faces the boss 73 (see FIG. 1) is inclined so as to be farther from the axis of the rotation shaft than the opening on the other end, and faces the boss 73. The opening of the one end face is provided outside the center of the eccentric bush 11.

Therefore, the moving speed of the refrigerant gas in the through hole 12 is slightly faster than that in the case of FIG.
The same effect as in the case (a) can be obtained.

FIG. 6A is a view showing an eccentric bush 21 according to a third embodiment of the present invention, and FIG. 6B is a view showing FIG.
It is CC sectional view taken on the line of FIG. The difference from the first and second embodiments is that the opening 22 at the other end of the through hole 21 has a recess 25 formed by a cutout at a portion that intersects the end face 24 at an obtuse angle. As with the second embodiment, the presence of the depression 25 facilitates the intake of the refrigerant gas into the opening 22. The taken refrigerant gas moves in the same manner as in the first and second embodiments, and the periphery of the eccentric bush 21 is lubricated by the lubricating oil contained in the refrigerant gas. still,
In the figure, reference numeral 26 denotes a pin insertion hole.

FIG. 7 is a view showing a modification of the eccentric bush 21 of FIG. FIG. 6 is a sectional view taken along the line CC of FIG.
Since it is the same as that shown in (b), illustration is omitted here. Parts corresponding to FIG. 6 are denoted by the same reference numerals. The opening of the through hole 22 on one end face facing the boss 73 of the eccentric bush 21 (see FIG. 1) is inclined so as to be further away from the axis of the rotation shaft than the opening on the other end, and faces the boss 73. The opening of the one end face is provided outside the center of the eccentric bush 21.

Therefore, the moving speed of the refrigerant gas in the through hole 12 is slightly higher than that in the case of FIG.
The same effect as in the case (a) can be obtained.

[0028]

As described above, according to the present invention, the refrigerant gas passes around the eccentric bush through the hole provided in the eccentric bush, so that the lubricating property is improved and the long life is achieved. A scroll compressor can be provided.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a scroll compressor according to a first embodiment of the present invention.

FIG. 2A is a view showing an eccentric bush of the scroll compressor of FIG. 1; (B) is a sectional view taken along line AA of (a).

FIG. 3 is a view showing a modification of the eccentric bush shown in FIG.

FIG. 4A is a view showing an eccentric bush according to a second embodiment of the present invention. (B) is sectional drawing which follows the BB line | wire of (a).

FIG. 5 is a view showing a modified example of the eccentric bush of FIG. 4 (a).

FIG. 6A is a view showing an eccentric bush according to a third embodiment of the present invention. (B) is sectional drawing which follows CC line | wire of (a).

FIG. 7 is a view showing a modification of the eccentric bush of FIG. 6 (a).

FIG. 8 is a sectional view showing a scroll compressor according to a conventional example.

FIG. 9 is a cross-sectional view illustrating a centrifugal pump provided in a conventional scroll compressor.

[Explanation of symbols]

 1,11,21 Eccentric bush 2,2,22 Through hole 5,15,26 Pin insertion hole 13 Projection 23 Opening 25 Depression

Claims (3)

(57) [Claims] A rotating shaft, an eccentric bush eccentric from the rotating shaft and coupled to one end of the rotating shaft, and a boss for rotatably accommodating the eccentric bush. In a scroll type compressor having a first spiral body orbiting and a second spiral body meshing with the first spiral body to obtain a compressing action of a refrigerant gas containing a lubricating oil, the eccentric bush may have a shaft. And a through-hole extending between both end surfaces in the direction, wherein the through-hole is inclined such that an opening on one end face facing the boss portion is farther from the axis of the rotating shaft than an opening on the other end face. It is located rearward of the opening of the one end face facing the boss in the circumferential direction of rotation of the rotating shaft, so that the flow of the refrigerant gas is caused in the through hole when the rotating shaft rotates. Characterized by Scroll type compressor. 2. The scroll type compressor according to claim 1, wherein the eccentric bush has a projection formed around the opening at the other end surface of the through hole for taking in refrigerant gas. A scroll type compressor characterized by the following. 3. The scroll compressor according to claim 1, wherein the eccentric bush is formed with a notch around the opening at the other end face of the through hole for taking in refrigerant gas. A scroll type compressor.