JPH02211397A - Oil separating mechanism for vane compressor - Google Patents

Abstract

PURPOSE:To improve the oil separation efficiency and suppress the swirling-up of stored oil by arranging a swirling-up preventing body in the lower part of a region between the right and left shielding bodies of a deflector and setting the guide shape for the coolant gas onto the both shielding bodies. CONSTITUTION:The coolant gas flow which is branched into the right and left parts by a deflector 20 collides with the right and left shielding plates 22 and 23 and branched into the upper and lower parts. The flow speed of the coolant gas is lowered by the blowing-collision, and the separation of mist form oil is generated. The downwardly branched flow is directed to the vicinity of the center of a swirling-up preventing plate 20 by the guiding shape of the shielding plates 22 and 23, and the downward coolant gas flows supplied from the right and left shielding plates 22 and 23 collide with the swirling-up preventing plate 24, and collide each other in the vicinity of the center in the lateral direction. Therefore, the coolant gas flow speed is reduced further, and also the separation of the mist form oil is generated, and the oil separation efficiency is improved. Further, the coolant gas whose speed is lowered by the swirling-up preventing plate 24 flows along the swirling-up preventing plate 24, and though a part collides with the stored oil surface in the lower part, the swirling-up of the stored oil surface is properly suppressed, since the sufficient speed reduction is performed.

Description

Detailed Description of the Invention [Industrial Field of Application] The present invention is directed to a rotor that is rotatably housed in a cylinder sandwiched between a front side plate and a rear side plate. The space is divided into multiple compression chambers by multiple vanes, and refrigerant gas is sucked in, compressed, and discharged by the rotation of the rotor, and oil is separated from the discharge chamber around the cylinder through the discharge passage on the rear side plate. This invention relates to an oil separation mechanism in a vane compressor that discharges refrigerant gas into a chamber.

[Prior Art] In a configuration in which an oil boule portion below an oil separation chamber is communicated with the bottom of a vane storage groove and the discharge pressure of the oil separation chamber is transmitted as back pressure to the vane via oil, the amount of oil stored in the oil pool portion is The lack of this results in a decrease in compression efficiency. Furthermore, poor lubrication of the sliding contact area caused by oil supply to the bottom of the vane housing groove is unavoidable. Therefore, it is necessary to efficiently return the mist-like oil contained in the refrigerant gas to the oil pool portion. Therefore, the
In the oil separation mechanism disclosed in Publication No. 2296, there is a shielding plate that connects the discharge chamber around the cylinder and the oil separation chamber and guides the refrigerant gas flow downward in front of the outlet of the discharge passage on the burnt plate. In addition, a roll-up prevention plate is provided below the shielding plate. As a result, the oil mist is separated by spraying the refrigerant gas onto the shielding plate, and the curling prevention plate prevents the downward flow of refrigerant gas from directly spraying the oil storage surface. If the refrigerant gas flow blows directly onto the oil storage surface, the stored oil will be rolled up by the refrigerant gas flow, and the amount of oil storage will quickly become insufficient.

Other oil separation mechanisms include, for example, one in which a curved plate surrounds the outlet of the discharge passage, a screen is provided in front of the outlet of the discharge passage, and a slit is provided at the bottom of the curved plate.

The refrigerant gas is guided along the inner peripheral surface of the curved plate, and the separated oil drips downward from the slit.

[Problems to be Solved by the Invention] However, in the former mechanism, although the anti-rolling plate prevents the downward flow of refrigerant gas, the flow rate of the discharged refrigerant gas is high in the high rotational region of the compressor, resulting in oil storage. The blowing action of the refrigerant gas flow against the surface is large, and a large amount of stored oil is stirred up. Moreover, the flow rate of the refrigerant gas is high (indeed, the oil separation effect by the shielding plate is also reduced, and the oil reduction efficiency is poor. Therefore, a shortage of oil storage is inevitable in the high-speed rotation region.

The latter mechanism has the drawback that the refrigerant gas and oil are vigorously agitated within the enclosed region, and in the high-speed rotation region, the oil is carried out of the compressor together with the refrigerant gas before it is separated.

SUMMARY OF THE INVENTION An object of the present invention is to provide an oil separation mechanism that can suppress the swirling up of stored oil while increasing oil separation efficiency.

[Means for Solving the Problems] To this end, in the present invention, a discharge refrigerant gas flow is guided to both sides in front of the outlet of the discharge passage in the rear side plate that connects the discharge chamber around the cylinder and the oil separation chamber. A deflector is installed, and shields are installed on the left and right sides of the deflector to vertically distribute the refrigerant gas flow distributed left and right by the deflector, and a wind-up prevention body is installed below the area between both shields. However, both the left and right shields are designed with guide shapes that direct the downward branching direction of the refrigerant gas toward the center of the left and right sides of the anti-roll-up body.

[Operation] The refrigerant gas discharged from the outlet of the discharge passage to the oil separation chamber is blown against the deflector and is divided into left and right directions by the deflector. The refrigerant gas flow divided to the left and right hits the left and right shielding plates, and is divided vertically by the shielding plates. This blowing reduces the flow rate of the refrigerant gas and causes separation of the oil mist. The downward branch flow is directed near the left and right centers of the hoisting prevention plate due to the guide shape of the shielding plate, and the downward refrigerant gas flows from both the left and right shielding plates collide with the hoisting prevention plate and collide with each other near the left and right centers. Fit. This collision further reduces the refrigerant gas flow velocity and also causes mist-like oil separation, increasing oil separation efficiency.

The refrigerant gas whose speed has decreased on the winding prevention plate flows along the winding prevention plate, and a portion of the refrigerant gas blows against the oil storage surface below the winding prevention plate. However, since the flow velocity of the refrigerant gas that blows onto the oil storage surface is sufficiently slowed down, the swirling up of the stored oil is appropriately suppressed.

[Example] Hereinafter, an example in which the present invention is embodied in a variable displacement vane compressor will be described based on FIGS. 1 to 6.

A cylinder 3 is housed and fixed in a pair of front and rear housings 1 and 2, and side plates 4.5 are tightly joined to both front and rear ends of the cylinder 3, and as shown in FIG. A cylindrical rotor 6 is rotatably supported. A plurality of grooves 7 are formed in the radial direction on the circumferential surface of the rotor 6, and a vane 8 is fitted and supported in each port 7 so as to be slidable approximately in the radial direction in close contact with both the front and rear side plates 4°5. ing.

An oil separation chamber R is formed between the rear housing 1 and the rear side plate 5, and an oil pool portion Rp is provided at the bottom of the oil separation chamber R. M7 communicates with the oil pool portion Rp via a supply passage 5a in the rear side plate 5, so that oil in the oil pool portion Rp can be supplied to the bottom of the groove 7. As a result, each vane 8 can come into contact with the circumferential surface of the cylinder chamber by the centrifugal force accompanying the rotation of the rotor 6 and the hydraulic pressure at the bottom of the groove 7, and the cylinder chamber is formed into a plurality of compression chambers p by the plurality of vanes 8.
A compartment is formed in l and p2.

As shown in Fig. 1.4, a pair of suction passages 9 and 10 are axially penetrated through the cylinder 3 at axially symmetrical positions, and a pair of discharge chambers 3a and 3b are axially symmetrically connected to the rear housing. 2 and cylinder 3. Suction passage 9.
10 communicates with the cylinder chamber via suction ports 11 and 12, and discharge chambers 3a, 3b communicate with the cylinder chamber via discharge ports 13, 14. The discharge port 13.14 is releasably closed by a discharge valve 15.16, and both ridge chambers 3a, 3b are connected to the oil separation chamber R via discharge passages 5b, 5c penetrating through the rear side plate 5. has been done. Therefore, the refrigerant gas introduced into the suction chamber 1a between the front housing 1 and the front side plate 4 is introduced into the cylinder chamber via the suction passages 4a and 4b of the front side plate 4 and the suction passage 9. The refrigerant gas discharged from the discharge ports 13.14 to the discharge chambers 3a, 3b by displacing the discharge valves 15.16 flows into the discharge passages 5b, 5.
The oil is discharged to the oil separation chamber R via c.

Inside the oil separation chamber R, the rear side plate 5 includes a flow path forming body 19 and a deflector 2 that constitute an oil separation mechanism.
0 are fastened together with screws 21. Discharge passage 5
Through holes 19a and 19b are penetrated through the portions of the flow path forming body 19 corresponding to the outlets b and 5c, and a deflector 20 having a U-shaped side cross section is disposed in front of the both passage holes 19a and 19b. ing.

A pair of shielding plates 22.23, which are part of the flow path forming body 19, are vertically arranged opposite to each other on both left and right sides of the deflector 20, and below the area between the two shielding plates 22.23. Similarly, a winding prevention plate 24, which is a part of the flow path forming body 19, is arranged to cover the oil pool portion Rp. The winding prevention plate 24 is formed in a shape that slopes downward to the left and right, and a guide surface 2 is provided on the lower side of the opposing surfaces of both shielding plates 22 and 23.
2a and 23a are formed to be inclined toward the center of the winding prevention plate 24.

As shown by the arrow P in FIG. 1, the refrigerant gas discharged from the discharge passages 5b and 5c to the oil separation chamber R hits the front wall of the deflector 20 and is divided into almost equal parts to the left and right, and the refrigerant gas that is divided to the left and right is shown in FIG. As shown by arrow Q, the shielding plate 22.
23 and the flow is split up and down. The collision with the shielding plates 22, 23 reduces the flow velocity of the refrigerant gas, and a portion of the mist-like oil in the refrigerant gas separates and drips. The separated and dripped oil is returned to the oil pool portion Rp between the left and right ends of the anti-rolling plate 24 and the inner peripheral surface of the rear housing 2. The upwardly diverted gas exits to the external refrigerant gas circuit through the outlet 2a, and the downwardly diverted gas flows along the guide surfaces 22a and 23a as shown by the arrow S in FIG.
It is directed towards the center of the left and right.

The refrigerant gas flow guided and deflected by the left and right shielding plates 22 and 23 toward the vicinity of the left and right center of the anti-rolling plate 24 collides with the anti-folding plate 24 and with each other, and the flow velocity is further reduced. Due to this flow rate reduction, the mist-like oil in the refrigerant gas is further separated and dripped, and together with the oil separation due to the collision of the refrigerant gas with the shielding plates 22 and 23, the separation efficiency becomes extremely high. The refrigerant gas flow guided downward by the guide surfaces 22a and 23a heads toward the center of the anti-rolling plate 24, and does not directly collide with the oil storage surface of the oil pool portion Rp. The refrigerant gas flow toward the oil pool part Rp is prevented from rolling up by the prevention plate 2.
Therefore, the proportion of the reservoir in the oil pool portion Rp that is rolled up by the refrigerant gas flow is lower than before, and combined with the good oil separation efficiency, the oil pool portion The decrease in Rp reservoir is moderately suppressed.

Furthermore, by tilting the anti-rolling plate 24 downward to the left and right, agitation of the refrigerant gas on the anti-rolling plate 24 is also suppressed, and oil separation on the anti-rolling plate 24 is performed more effectively.

In FIG. 6, a curve C1 shows the oil level in the oil pool portion Rp of this embodiment, and the amount of oil stored is kept almost constant even in the high speed rotation region of the compressor. A curve C2 shown by a chain line represents the oil level change due to the conventional oil separation mechanism, and the difference from this example is obvious. The good oil storage amount maintenance effect as in this embodiment prevents oil from running out between the bottom of the groove 7 that accommodates the vane 8 and the oil pool portion Rp (and maintains good pressure transmission to the bottom of the vane 8). bring.

This does not cause a decrease in compression efficiency, and does not cause poor lubrication at the sliding contact portion due to oil supply to the bottom of the groove 7.

In this embodiment, an annular capacity control plate 25 is rotatably interposed between the rotor 6 and the front side plate 4, and a pair of pressure chambers s are connected via a spool 26 as shown in FIG.
1. The rotation of the capacity control plate 25 is controlled by the pressure resistance between s2, and a pair of auxiliary passages 25a (only one shown) on the capacity control plate 25 connects the suction passage 4a and the cylinder chamber. It is set in. Therefore,
By rotating the capacity control plate 25, the compression chambers P1 and P2 are
The period of communication between the cylinder and the auxiliary passage 25a is changed, thereby controlling the suction volume into the cylinder chamber, that is, the volume discharged into the discharge chambers 3a and 3b. This control is performed by supplying discharged refrigerant gas to the pressure chamber S2 and supplying oil from the oil pool portion Rp to the pressure chamber S1. 25
Rotation control is performed appropriately, and good capacity variable control is performed.

The present invention is of course not limited to the embodiments described above, and embodiments shown in FIGS. 7 to 9, for example, are also possible.

In the embodiment shown in FIG. 7, the flat shielding plates 27.28 are formed at an angle so as to widen at the upper side.
The refrigerant gas that collided with 8 flows upward to some extent. The refrigerant gas flow branched downward upon hitting the shielding plates 27, 28 is directed near the center of the anti-rolling plate 24, as in the previous embodiment, thereby preventing direct collision with the oil pool portion Rp and decelerating the refrigerant gas flow.

In the embodiment shown in FIG. 8, the lower sides of the shielding plates 29 and 30 are inclined so as to point near the left and right center of the winding prevention plate 24, and the upper sides are inclined inward, and the boundary between the upper and lower slopes is the deflector. It is set on the left and right extension line of 20. Therefore, the deceleration effect by the shielding plates 29 and 30 is greater than in the previous embodiments, and the oil separation effect is also enhanced.

In the embodiment shown in FIG. 9, the shielding plates 31.32 are formed in an arc shape, and the downward branch of the refrigerant gas that collides with the shielding plates 31.32 is directed toward the center of the anti-rolling plate 33. A plurality of through holes 33a are provided at both left and right end portions of the winding prevention plate 33, and the refrigerant gas flow along the winding prevention plate 33 is slowed down by the through holes 33a, thereby improving oil separation efficiency.

Further, in the present invention, a flat roll-up prevention plate is disposed horizontally, and as shown in FIG. An embodiment in which an integral part with .37 is assembled is also possible. Note that 34 is an auxiliary plate for forming a flow path, and a protruding piece 34a on the lower side thereof and a protruding piece 35a on the lower part of the deflector 35 are spot welded.

Furthermore, in the present invention, embodiments such as forming the deflector integrally with the shielding plate and the winding prevention plate, or forming the shielding plate and the winding prevention plate separately, are also possible.

Further, the present invention is also applicable to a vane compressor without a variable capacity mechanism.

[Effects of the Invention] As detailed above, the present invention distributes the discharged refrigerant gas flow to the left and right by the deflector in front of the outlet of the discharge passage in the rear side plate, and distributes the distributed refrigerant gas flow to the left and right shields. In addition to dividing the flow upward and downward, the downward flow is directed toward the center of the anti-rolling plate, so the refrigerant gas flow is decelerated by the shielding plate, and the downward flow of flow is prevented from colliding directly with the oil storage surface. This provides an excellent effect in that oil separation due to gas flow deceleration and oil rolling up from the oil pool portion are appropriately suppressed.

[Brief explanation of the drawing]

1 to 6 show one embodiment embodying the present invention, FIG. 1 is a side sectional view of the entire compressor, and FIG. 2 is a line AA in FIG.
3 is an exploded perspective view of essential parts, 4 is a sectional view taken along line B-B in 1, 5 is a sectional view taken along line C-C in 1, and 6 is an oil level. Graphs showing changes in , and Figures 7 to 10 are all exploded perspective views of essential parts of the present invention.

Claims (1)

[Claims] 1 The space between the circumferential surface of a rotor rotatably housed in a cylinder sandwiched between a front side plate and a rear side plate and the inner circumferential surface of the cylinder is divided into a plurality of compression chambers by a plurality of vanes, and the rotor In a vane compressor that suctions, compresses, and discharges refrigerant gas by the rotation of the cylinder, and also discharges refrigerant gas from a discharge chamber around the cylinder to an oil separation chamber through a discharge passage in a rear side plate, an outlet of the discharge passage A deflector is disposed in front of the deflector to guide the discharged refrigerant gas flow to both sides, and shields are disposed on the left and right sides of the deflector to distribute the refrigerant gas flow distributed left and right by the deflector in the vertical direction. In a vane compressor, a winding prevention body is arranged below the area between the bodies, and a guide shape is set on both the left and right shields to direct the downward branching direction of the refrigerant gas to the vicinity of the left and right center of the winding prevention body. Oil separation mechanism.