JPS60135690A - Oil supplying device for vane rotating type compressor - Google Patents

Abstract

PURPOSE:To permit stabilized operation even upon starting from pressure equalized condition by a method wherein lubricating oil in a space accommodating vanes is discharged by a centrifugal effect of the rotation of the vanes and is permitted to be supplied into a space at the backside of the vanes through an oil supplying path. CONSTITUTION:The lubricating oil in an oil reservoir space formed by a shaft 4 and a rear side plate 6 is discharged upon starting from the pressure equalized condition by the centrifugal effect of the rotation of the vanes 10 provided on the shaft 4 rotating together with a rotor 2, therefore, the lubricating oil may be supplied to the backside of the vanes 3 surely. According to this method, the defect of conventional vane rotating type compressor, in which the vanes 3 are separated from the inner wall of a cylinder 1 and are pushed into a vane slot thereby causing poor compression, may be eliminated while deterioration of abrasion resisting property of the tip end of vane and increase of torque, which are generated in case an expensive oil pump is used, may be eliminated whereby the stabilized operation may be effected.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to an oil supply device for applying pressure to the vanes of a vane rotary compressor, especially an automobile engine which starts and stops frequently and starts at a low rotation speed. The present invention relates to an oil supply device for a vane rotary compressor driven by a possible drive source.

Conventional configuration and problems As is well known, in vane rotary compressors, high pressure is applied to the rear end of the vane so that the vane always rotates and slides with its tip in contact with the inner wall of the cylinder as the rotor rotates. A structure that applies lubricating oil is used.

As one means of achieving this, inside a high-pressure sealed case,
! : A passage is provided that communicates with the oil supply groove provided on the side of the O-tor, and by supplying oil to the back space of the vane by differential pressure, a pressing action is exerted on the rear end of the vane, and the oil supply groove is connected to high pressure gas. A partially separated structure is known in which oil supply to the back space of the vane is cut off in order to prevent a malfunction in which the vane tip separates from the cylinder inner wall at the low-pressure gas boundary (axial seal point). As a result, the vane tip always rotates and slides in contact with the cylinder inner wall during operation.

For example, if we consider the case where the above-mentioned conventional compressor is used in an automobile refrigeration cycle, the compressor is driven by an engine, but the engine has a wide range of rotational speeds (60 o
r,p,m to 6000r,p,m), the rotational speed of the compressor also varies over a wide range.

On the other hand, the refrigeration cycle consists of a compressor, a condenser, and a liquid receiver.

It consists of an expansion valve and an evaporator connected by piping,
When the compressor is stopped, leakage from the throttle part of the expansion valve or the discharge valve installed in the discharge type that opens into the internal space of the compressor cylinder may occur over time after the compressor is stopped. The entire frozen cycle becomes under equal pressure. In addition, it usually takes about 1 to 2 hours to reach a pressure equalization state, and therefore, under extremely common operating conditions, it is common for the entire interior of the compressor to reach an equal pressure state. I am in a state where I can get it.

However, as mentioned above, in the conventional compressor, oil is supplied to the space behind the vane using the pressure difference inside the compressor.
When starting the compressor when the refrigeration cycle is in an equal pressure state 1 to 2 hours after the compressor has been stopped, the back of the vane is not sufficiently lubricated, and therefore the vane absorbs the cylinder inner wall force and This has the disadvantage that it becomes loose and gets pushed into the vane slot, causing poor compression.

Of course, in this case, centrifugal force acts on the vane in the direction of extension depending on its rotational speed, but at low rotational speeds (for example, 1 o
o o r, p, m or less), this effect is extremely small, and therefore, the effect of centrifugal force cannot be expected in compressors for automotive refrigeration cycles, which are likely to be started at low rotational speeds.

In addition, in order to prevent the drawbacks seen in the conventional compressors mentioned above, there is a configuration in which lubricating oil is supplied from an oil reservoir below the high-pressure case by an oil pump attached to the rear part of the support shaft that rotates with the rotation of the rotor. In this configuration, as the rotation speed increases, the supply oil pressure increases, and the pressure applied to the rear end of the vane also increases sharply. Therefore, the vane tip is pressed excessively against the cylinder inner wall, causing an increase in surface pressure and reducing wear resistance. A phenomenon of deterioration of gender occurs. In addition, since the oil pump is constantly operating during operation, the torque required to operate the oil pump increases, especially at high rotational speeds, which increases the torque of the entire compressor, lowering efficiency, and adding cost to the oil pump. It costs as much as it takes.

Purpose of the Invention The present invention eliminates the drawbacks found in the conventional compressors mentioned above, does not cause deterioration of the wear resistance of the vane tips, does not reduce the efficiency of the compressor, is low cost, and can be used when starting from an equal pressure state. The purpose is to enable stable operation.

Structure of the Invention In order to achieve this object, the present invention provides blades that rotate with the rotation of the rotor inside the rotor support part supported by the rear side plate and in the space formed by the rear side plate and the rotor support part. The space in which the blades are housed is communicated with an oil supply groove provided on the side surface of the rotor through an oil supply passage.

With this configuration, when the entire refrigeration cycle is started from an equal pressure state, the lubricating oil existing in the space where the blades are housed is discharged by the centrifugal action of the blades that rotate with the rotation of the rotor, and The space behind the vane can be supplied with oil through the passage, which creates a suppressing effect on the rear end of the vane, preventing poor compression in which the vane separates from the inner wall of the cylinder and is pushed into the vane slot. This ensures reliable external compression and allows continuous oil supply from the oil reservoir due to the pressure difference inside the compressor.

DESCRIPTION OF THE EMBODIMENTS An embodiment of the present invention will now be described with reference to FIGS. 1 to 4.

In the figure, a vane rotary compressor is used, and the cylinder 1 has a cylindrical inner wall, and a part of the outer peripheral surface of the cylinder 1 always forms a slight gap between the inner wall of the cylinder 1 and the axial seal point. a rotor 2 disposed in the rotor 2; two plates 73 which are inserted into two vane slots provided in the rotor 2 so as to be retractable and whose tips disintegrate into contact with the inner wall of the cylinder 1; and two plates 73 which are fastened to the rotor 2. A front side plate 6 and a rear side plate 6 that rotatably support the integrated shaft 4 and close both end faces of the cylinder 1 to form an internal cylinder space communicate with a discharge hole 7 that opens into the cylinder internal space. The compressor body is constituted by a high pressure case 8 having an oil reservoir below. Further, the rear side plate 6 is provided with an oil supply groove 9 communicating with the vane back space formed by the vane slot and the rear end of the plate 73. In addition, in this compressor main body, the oil supply groove 9 and the oil sump part below the high pressure case 8 are communicated via the oil supply hole 12 for differential pressure, and high pressure from the high pressure case 8 is applied to the rear end of the bay 73. A refueling passage is provided through which the bevel 73 protrudes, and vanes 10 are installed inside and at the rear end of the shaft 4 which is fastened and integrated with the rotor 2 . Shaft 4 and rear side plate 6
The oil reservoir space formed by the above is in communication with the oil supply counterfeit 9 via the blade oil supply hole 13.

As a result, at the time of startup, the lubricating oil in the oil reservoir space formed by the shaft 4 and the rear side plate 6 is transferred to the oil supply hole 13 and It is added to the rear end of the vane 3 via the oil supply groove 9 to make the vane 3 protrude.

Note that 11 is an oil case, and 14 is a nozzle for adjusting the amount of oil. 15 is a two-part case, 16 is a rear bearing,
17 is a front bearing, and 18 is a mechanical seal.

In the above configuration, the lubricating oil in the oil sump space formed by the shaft 4 and the rear side plate 6 is discharged at the time of startup due to the centrifugal action of the blades 10 installed on the shaft 4, which rotates together with the rotor 2. It is possible to reliably supply oil to the back of the base 73, and it is possible to prevent poor compression at startup, which has been seen in the past.

Furthermore, after the lubricating oil in the oil sump space formed by the shaft 4 and the rear side plate 6 is discharged during startup, no lubricating oil is specially supplied to the space, and the blade 1Q becomes idle. Therefore, the torque required to rotate the blade 1◯ is almost unnecessary, and the drawbacks seen in the conventional oil pump type oil supply can also be avoided.

In addition, after normal compression occurs after startup, due to the pressure difference inside the compressor, the high pressure case 8, which is the conventional oil supply passage,
Oil is supplied from the oil reservoir below.

During operation, lubricating oil is not specially supplied to the oil reservoir space formed by the shaft 4 and the rear side plate 6, but when the compressor is stopped, lubricating oil is supplied from the oil supply groove 9 and the high pressure case 8 due to the pressure difference. The oil flows back into the oil sump space and fills it. Therefore, lubricating oil is secured to be discharged from the oil sump space when the engine is started after stopping.

In this embodiment, the blade 1O installed on the shaft 4 is a curved blade with a sheet metal structure, but the blade is not limited to this, and may be a resin product, a cast product, etc. as long as it has a structure that discharges lubricating oil by rotational centrifugal action. Regardless of the material. Alternatively, the blade structure may be formed directly on the rear end of the shaft 4.

Effects of the Invention As is clear from the embodiments described above, the present invention provides blades that rotate with the rotation of the rotor in the back space of the rotor support, and a space in which the blades exist and a lubrication groove provided on the side surface of the rotor. are connected through an oil supply passage, and when the entire refrigeration cycle is started with equal pressure, the lubricating oil in the space where the vane exists is reliably supplied to the space behind the vane by the rotating centrifugal action of this vane. This eliminates the disadvantages of conventional vane rotary compressors, where the vanes come loose from the cylinder inner wall and are forced into the vane slots, causing poor compression. It can be manufactured at low cost without the phenomenon of deterioration of wear resistance of the vane tip or increase of torque that occurs in the case of vanes.

[Brief explanation of drawings]

Fig. 1 is a side sectional view of a vane rotary compressor having an oil supply device showing an embodiment of the present invention, Fig. 2 is a sectional view taken along line u-■ in Fig. 1, and Fig. 3 is a sectional view of The enlarged view of part B and FIG. 4 are perspective views of blades in the same compressor. 1... Cylinder, 2... Rotor, 3...
...Vane, 4...Shaft, 6...
...Front side plate, 6...Rear side plate, 7...Discharge hole, 8...High pressure case, 9...Oil supply groove, 1o...・Blade, 11... Oil case, 12... Oil supply hole for differential pressure, 13...
Oil supply hole for the blade. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure 2/? 3

Claims (1)

[Claims] A cylinder having a cylindrical inner wall, a rotor disposed within the cylinder such that a part of its outer peripheral surface always forms a minute gap between the inner wall of the cylinder and a small axial seal point, and this rotor. A plurality of vanes are inserted into and retractably into a plurality of vane slots provided in the cylinder, and the tips of the vanes abut against the inner wall of the cylinder. A compressor main body is constituted by a front side plate and a rear side plate, and a high pressure case that communicates with a discharge hole opening into the cylinder interior space and has an oil reservoir below, and further includes a vane slot and a vane formed in one side plate. An oil supply groove communicating with the vane back space formed by the rear end is provided, and the oil supply groove is communicated with an oil reservoir portion below the high pressure case to apply high pressure from the high pressure case to the rear end of the vane. An oil supply passage for protruding the vane is provided, and a vane is provided inside the support part of the rotor supported by the rear side plate and at the rear end, and the oil supply groove and the vane are provided in the space formed by the rear side plate and the rotor support part. A vane rotary compressor oil supply system with a communicating oil supply passage.