JPS61116087A - Vane-type compressor - Google Patents

Abstract

PURPOSE:To put the central location of a rotor in the shaft orientation rightly by leading lubricating oil into space between the end face of the rotor and side faces of both the rear-side and front-side plates and thereby forming fluid static pressure bearing parts there. CONSTITUTION:On the rear-side plate 2 of a vane-type compressor, an oil passage having an opening on a connecting groove 16 is formed, while oil passages 17, 18 with their one ends communicated with the connecting groove 16 and their other ends having openings on the side faces of a plate confronting the end face of the rotor and also shaped. With lubricating oil flowing out of small holes 17, 21, fluid static pressure bearings are formed in space 41 between the end face of the rotor and the side face of the front-side plate and space 42 between the end face of the rotor and the side face of the rear-side plate. Therefore, the central position of the rotor in the shaft orientation can be rightly adjusted.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a vane compressor used in automobile air conditioners and the like, and particularly to a structure for positioning the center of a rotor in the axial direction.

[Background of the invention]

In a vane compressor, when an external force in the axial direction is applied to the drive shaft, the rotor tends to shift from its axial center position. Particularly in vane compressors used in automobile air conditioners, a belt and an electromagnetic clutch are attached to one end of the drive shaft, so when this electromagnetic clutch is energized, the drive shaft and eventually the rotor move away from the axial center position. It will shift. Therefore, in a vane type compressor, a means for appropriately positioning the rotor at the axial center position is required. Regarding the axial center positioning of this rotor,
There is a device disclosed in Japanese Patent Application Laid-Open No. 48-20107, but this has a complicated means for holding the rotor at the center position.

[Object of the Invention] An object of the present invention is to provide a vane compressor that has a simple structure, can appropriately control the axial center position of the rotor, and has high performance and reliability.

[Summary of the invention]

Normally, in a vane compressor, a small gap is formed between the rotor end face and the rear side plate side and between the rotor end face and the front side plate side from the viewpoint of productivity2 and ease of assembly. . Therefore, the present invention forms a hydrostatic pressure bearing part in the gap by guiding lubricating oil under discharge pressure into the gap, so that the rotor is properly positioned at the center position in the axial direction. It is something.

[Embodiments of the invention]

An embodiment of the present invention will be described below with reference to FIGS. 1 to 3. FIG. 1 is a longitudinal cross-sectional view of a vane compressor according to the present invention, and FIGS. 2 and 3 are plan views of a rear plate and a front plate in FIG. 1. In FIG. 1, a chamber formed by a front 9111 plate 1, a rear 1i111 plate 2, and a cam ring 3 fastened between both plates by bolts (not shown) includes a plurality of cam rings that can move forward and backward in the radial direction. A rotor 5, which looks over the vanes 42 and vane grooves in which each vane is accommodated, is rotatably arranged concentrically with the axial center of the cam ring 3. Rotor 5 was fixed. The drive shaft 6 is supported by the front plate 1 and the rear plate 2 by needle bearings 7. In addition, the front (i11
The plate 1, the rear plate 2, and the cam ring 3 are fixed to a front cover 8 by through bolts (not shown), and the periphery thereof is covered by a chamber 9. The front cover 8 and the chamber 9 are kept airtight by an O-ring 10, and a rotor 11 coupled to the drive shaft 6 and a cover plate 12 fixed to the front cover 8 form a shaft seal. There is.

The chamber 9 has a space 1 behind the rear plate 2.
3 and an oil reservoir 30 below the space 13.
fc is formed. Further, an oil separator 14 is installed in the space 13 so as to cover the rear plate 2.

The rear plate 2 is provided with an oil supply passage 15 which has one end open to an oil reservoir 30 and the other end to a ring-shaped communication groove 16 provided on the outer periphery of the needle bearing 7. Oil supply passages 17 and 18 are provided which are in communication with the communication groove 16 and whose other ends are open on the side surface of the plate facing the end surface of the rotor. Also, the front plate 1 and the rear plate 2 are provided with an oil supply passage 19, a ring-shaped communication groove 20, and an oil supply passage 221.
22 is provided, and the oil supply passage 1 of the rear side plate 2
5 and the oil supply passage 19 of the front side plate 1 are the oil supply passage 2 provided across both plates 1 and 2 and the cam ring 3.
It communicates via 3.

Here, regarding the flow of refrigerant in this compressor, the refrigerant returned to the compressor from the refrigeration cycle flows into the low pressure passage 25 of the front cover 8 through the suction port 24 provided in the front cover 8. After the refrigerant passes through an intake port (not shown) provided on the front plate 1, it passes through two adjacent vanes 4, the outer peripheral surface of the rotor 5, and the cam ring 3.
It flows into the compression chamber 26 formed by the inner peripheral surface. The volume of the compression chamber 26 first changes from 0 to the maximum value as the drive shaft rotates 60 times, and the intake stroke ends.Furthermore, as the drive shaft rotates, the compression chamber volume gradually decreases from the maximum value. The compressed refrigerant reaches a discharge pressure and is discharged into the oil separator 14 through a discharge boat 27 and a discharge valve 28 provided in the cam ring 3.

Here, the refrigerant from which the oil has been separated is pumped through a compressor discharge port 29 provided in the chamber 9 to the refrigeration cycle.

The lubricating oil separated by the oil separator 14 and under discharge pressure is once stored in an oil reservoir 30 at the bottom of the chamber.
Due to the pressure difference between the pressure inside the chamber 9 and the pressure inside the compression chamber 26, the refrigerant flows into the oil supply passage 15 of the rear side plate 2, and in the rear side plate 2, the refrigerant passes from the oil supply passage 15 through the communication groove 16, and then An oil groove 31 formed in the compression chamber 26 and in the rear plate 2 via the oil supply passages 17 and 18.
flows out to. On the other hand, in the front side plate 1, the refrigerant flows from the oil supply passage 15 to the oil supply passage 23 and the oil supply passage 19.
, and then flows out into the compression chamber 26 and the oil groove 32 via the oil supply passages 21 and 22.

Next, FIG.
This will be explained with reference to FIG.

In FIG. 2, the oil supply passage 18 of the rear side plate 2 is
The openings 18a of both small holes 18 are 180 degrees symmetrical with respect to the drive @6, and the vane 4
It is provided at a position where the tip communicates with the vane groove bottom 33 when the tip reaches the discharge boat 27 of the cam ring 3. The oil grooves 31 are formed in a fan shape, and are provided at positions 180 degrees symmetrical about the drive shaft 6 and in communication with the bay/groove bottom portion 33. Regarding the starting point position of the oil groove 31' in the rotor rotational direction, normally, on the inner circumferential surface of the cam ring 3 closest to the outer circumferential surface of the rotor 5,
For the purpose of ensuring compression performance, a circular arc portion concentric with the rotor center is formed with a radius slightly larger than the rotor outer diameter.

When the tip of the vane 4 comes into contact with the end point position of the cam ring arc in the rotor rotation direction, the bottom part 33 of the vane groove contacts the oil groove 3.
It is designed to open at 1. In other words, when the vane 4 passes through the cam ring arc portion and the bee 1/4 pops out from inside the rotor, the pressure in the oil groove acts as a force (hereinafter referred to as vane back pressure) that presses the bee 74 against the inner peripheral surface of the cam ring 3. I am trying to apply it.

That is, focusing on the vane groove bottom 33, when the vane tip reaches the discharge boat 27, the vane groove bottom 33 communicates with the small hole 18, and the vane groove bottom 33 communicates with the small hole 18 at the starting point of the cam ring arc in the rotor rotation direction. The small hole 18 and the oil groove 31 do not communicate with each other at the arcuate portion, but communicate with the oil groove again immediately after the end position of the arcuate portion.

On the other hand, the oil supply passage 17 also consists of two small holes, and the openings 17a of both the small holes 17 are located 180 degrees symmetrically about the drive shaft 6, and are located near the rotor outer periphery and do not communicate with the vane groove bottom 33. It is set in.

In FIG. 3, the oil supply passage 21 of the front side plate 1
．． 22 and the oil groove 32 have the same shape and position as those of the rear plate 2.

In addition, the opening of the small hole 21.22 forming the oil supply passage has a hole 21a.
, 22a with the explosion number 1. Next, the means for determining the pressure within the oil groove will be explained. When the bay 74 reaches the discharge boat 27 installed on the cam ring (see Fig. 2), the small hole 18 and the oil groove 3 are connected through the bay 7 groove bottom 33.
1 is connected. Therefore, the pressure inside the oil groove at this point is the pressure inside the small hole 18 via the valley/groove bottom 33f (the pressure inside the small hole 18 is approximately equal to the compressor discharge pressure). is guided.

However, because the time during which the small hole 18 and the oil groove 31 are in communication is short, and because the oil actually passes through the gaps between the rotor and the rear and front side plates, the pressure inside the small hole 18 will be lower than the pressure inside the small hole 18. . When the rotor 5 rotates from this state (clockwise in FIG. 2) and the vane groove bottom 33 separates from the oil groove 31, there is no communication with the small hole 18 through the vane groove bottom and the rotor The pressure inside the oil groove gradually begins to decrease due to leakage from the gap between the plates on both sides. That is, the pressure inside the oil groove increases rapidly at the moment when the small hole 18 and the oil groove communicate through the bottom of the vane groove, and gradually decreases when the communication is lost.

However, since this phenomenon occurs at a cycle of (number of compression chambers) x (number of vanes) = 10 times per rotor rotation, the actual oil groove pressure is averaged by the above phenomenon, and the compressor discharge The pressure will be approximately between the pressure and the suction pressure of the machine.

This also applies to the small holes 20 and oil grooves 32 in the front plate 1.

On the other hand, since the small holes 17 and 21 communicate with the communication grooves 16 and 20 provided on the outer periphery of the needle bearing, the pressure in both small holes is reduced by the discharge of the compression chamber as in the small holes 182 and 22. The pressure is almost equal to the pressure. Therefore, due to the lubricating oil under high pressure flowing out from the small holes 17 and 21, fluid flows into the gap 41 between the rotor end face and the front plate side face and the gap 42 between the rotor end face and the rear plate side face shown in FIG. A hydrostatic bearing is formed.

The lubricating oil also performs a lubricating and sealing action on the arc portion of the cam ring 3 and the gaps 41 and 42 described above.

Therefore, in the vane compressor according to the present invention, some external force acts on the drive shaft 6, causing the rotor 5 to move to the first position.
If it moves to the left in the figure, for example, it is used as a compressor for an automatic heavy-duty air conditioner, and the drive shaft 6 and hence the rotor 5 move to the left due to the excitation of the electromagnetic clutch attached to one end of the drive shaft 6, and the rotor 5 moves to the left. 5 deviates from the axial center position, the gap 41 becomes smaller and the gap 42 becomes narrower.

Therefore, in the gap 41 the pressure under the square increases and in the gap 42 the pressure drop decreases. Here, the gaps 41 and 42
Since the pressure of the compressed amount passing through and flowing in is the same, the pressure inside the small hole 21 increases, and the pressure inside the small hole 17 decreases. The pressure difference causes the rotor 5 to be pushed back to the right, ie to the center position, and the forces on the rotor 5 are again in equilibrium.

On the other hand, the small holes 18 and 22 are used as vane back pressure, but like the small holes 17 and 21, they also function as hydrostatic bearings. That is, the openings of the small holes 17 and 21 are located near the outer periphery of the rotor 5, and the small holes 1
Since the openings 8 and 22 are provided inside the rotor 5, they can more effectively function as a hydrostatic bearing.

4 and 5 show other embodiments of the present invention, FIG. 4 is a plan view of the rear plate, and FIG. 5 is a sectional view taken along the line A--A in FIG. 4. In this embodiment, a rectangular groove 50 that is continuous with the opening 17a of the small hole 17 is provided on the side surface of the rear plate 2 in the radial direction of the rotor. To explain in detail, the groove 50 has a pt@ of the small hole 17.
It is slightly larger than the opening diameter of the vane groove 33 (in Fig. 4, the vane groove bottom 33 is circular, but the bottom of the vane groove is circular). In the case of a rectangular shape, it is formed so as to be outside the circle inscribed in the bottom of the vane groove. Also, groove 5
The circumferential position of 0 is determined by the position of the upper small hole 17.

Therefore, the lubricating oil passes through the communication groove 16 and the small hole 17, passes through the gap between the tank 6n and the tank 6n, and reaches the compression chamber. Here, the oil stored in the groove 50 is used as a hydrostatic pressure bearing, and also on the high pressure side and the low pressure side of the compression chamber (in FIG. 4, the low pressure side is separated from the place where the groove 50 is provided). A compression chamber and a high pressure side compression chamber are formed).

Although not shown, the front plate is also provided with grooves similar to those described above.

As described above, according to this embodiment, it is possible to expand the effective bearing area and to lengthen the gas line 7.

6 and 7 also show other embodiments of the present invention, FIG. 6 is a plan view of the rear side pulley vh, and FIG. 7 is a sectional view taken along the line B-B in FIG. 6. There is. In this embodiment, a rectangular groove 50 connected to the opening 17a of the small hole 17 is provided on the side surface of the rear plate 2 in the circumferential direction of the rotor. Further, the groove 50 has approximately the same length as the arc length of the circular arc portion formed in the cam ring 3. Incidentally, a groove similar to that described above is also provided on the side surface of the front side plate.

Therefore, in this embodiment as well, the effective bearing area can be expanded, and the oil flowing into the groove performs gas sealing in the gaps between the rotor and the rear and front side plates, as well as gas sealing in the arc portion of the cam ring. , 7- The stability is improved.

〔Effect of the invention〕

As explained above, according to the present invention, the axial center position of the rotor can be controlled excessively with a simple structure, thereby improving performance and reliability.

[Brief explanation of drawings]

1 to 3 show one embodiment of the present invention, FIG. 1 is a longitudinal sectional view of a vane compressor according to the present invention, and FIGS. 2 and 3 are plan views of the rear plate in FIG. 1. 4 and 5 show other embodiments of the present invention, FIG. 4 is a plan view of the rear plate, and FIG. The sectional view, FIGS. 6 and 7 also show other embodiments of the present invention, FIG. 6 is a plan view of the rear plate, and FIG. 7 is a sectional view taken along the line B-B in FIG. 6. . DESCRIPTION OF SYMBOLS 1...Front side plate, 2...Rear side plate, 3...Cam ring, 4...Vane, 5...Rotor, 6...Drive shaft, 9...Chamber, 13...・Space, 15° 19...Oil supply passage, 17.21...Small hole (oil supply passage), 17a, 21a...Opening, 30.
...Oil sump, 41°42...Gap, 50...Groove. Employment 1 cause'#2

Claims (3)

[Claims] 1. A working chamber formed by a cam ring, a rear plate and a front plate installed to close the cam ring and both end surfaces thereof, a plurality of vanes that can move forward and backward in the radial direction, and a vane groove that accommodates each vane. a rotor rotatably disposed in the working chamber so as to be rotatable concentrically with the axial center of the cam ring; a drive shaft that fixes the rotor to rotate the rotor; and a space behind the rear plate. and a chamber formed with an oil reservoir for storing lubricating oil at the bottom of the space, and the pressure difference between the pressure inside the chamber and the discharge pressure of the compression chamber formed by the cam ring and the vane. Therefore, in the vane compressor configured to supply lubricating oil from the oil reservoir to each bearing of the drive shaft through the passage, one of the rear side plate and the front side plate faces the end surface of the rotor. Lubrication passages are provided that are open on the side of the plate and the other side communicates with the passage, and lubricating oil is introduced into the gap between the rotor end face and the rear side plate side and the gap between the rotor end face and the front side plate side through each oil supply passage. 1. A vane type compressor, characterized in that a hydrostatic pressure bearing portion is formed in the gap by swinging. 2. Each of the above-mentioned oil supply passages is composed of at least two small holes, and the openings of both small holes are provided at positions symmetrical about the drive shaft and at positions that do not communicate with the bottom of the vane groove. A vane compressor according to claim 1. 3. A patent characterized in that a side surface of the rear side plate and a side surface of the front side plate are provided with a groove connected to the opening of the small hole, and the cross-sectional area of the groove is larger than the cross-sectional area of the small hole. A vane compressor according to claim 2.