JPS6360231B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vane type compressor, and is particularly effective as a refrigerant compressor for use in automobile air conditioners.

Generally, this type of compressor has a working chamber formed by the outer circumference of the rotor, the side surface of the vane, and the inner surface of the housing.
It is designed to perform compressed discharge. The vanes are then housed in vane grooves formed in the rotor. This vane groove was formed over the entire length of the side surface from the end surface of the rotor in order to particularly facilitate machining.

However, according to the experimental studies conducted by the present inventors, a problem was discovered in which the rotor stuck to the inner surface of the housing near the end surface on one end side of the rotor. After various studies on the cause of this, we found that
This is due to the following reasons:
It was confirmed.

That is, in this type of compressor, liquid refrigerant may be present in the working chamber, especially at the time of startup, and if the compressor is started in this state, liquid compression will occur, causing the pressure in the working chamber to become abnormally high. Therefore, as shown in FIG. 1, an abnormally high pressure is applied to the side surface of the vane 1, and this pressure is applied to the side surface of the groove 2 so as to push the vane groove 2 open. The groove 2 is pushed open by this force, and in particular, since the groove 2 has a shape in which a hole is opened at the end face on one end side, the amount of pushing open at the end face on the one end side increases. Therefore, the outer surface of the rotor 3 is pressed against the inner surface of the housing 8 at this one end side end surface, causing galling between the rotor 3 and the housing 8.

The present invention has been devised in view of the above points, and an object of the present invention is to prevent galling between rotor housings and to enable stable operation of a compressor over a long period of time.

Therefore, the compressor of the present invention adopts a configuration in which the rotor is shaped into a cylindrical shape in which the end face on one end side has a slightly smaller diameter than the other end side.

Therefore, in the compressor of the present invention, even if the end face of one end of the rotor is pushed open due to temporary pressure or liquid compression, the outer surface of the rotor is not pressed against the inner surface of the housing due to the pushing open. This prevents galling between the rotor and housing.

Next, an embodiment of the compressor of the present invention will be described based on the drawings.

First, the components of the compressor will be explained based on FIGS. 2 to 5. In the figure, 5 is a drive shaft, 3 is a rotor formed integrally with this shaft 5, and the shaft 5 rotor 3 is made of a ferrous metal material. A vane groove 2 is formed in the rotor 3 in a cross shape from an end surface 3a on one end thereof. A vane 1 is slidably disposed in the vane groove 2 and has a substantially U-shape, and the wall thickness of the central portion 1a is thinner than the wall thickness of the vane main body portion 1b. The tip portion 1c of the vane 1 has a tapered shape that is somewhat thin. A rotor cover 6 covers one end surface of the rotor 3, and is connected to a screw hole formed in the rotor 3 via a bolt 7.

As shown by the broken line in FIG. 4, the rotor 3 has an outer surface tapered such that one end surface 3a has a slightly smaller diameter than the other end surface 3b. However, if the angle α of this taper becomes too large, the sealing of the outer surface of the rotor 3 will be poor, so the angle is extremely small. That is, while the rotor width L is about 35 mm, the difference between the rotor one end diameter B and the other end diameter A is about 0.005 mm.

Similarly, the vane cover 6 is also attached to the rotor one end side 3.
It has a tapered shape that becomes smaller in diameter toward the a side.
This taper angle β is also extremely small, and when the cylindrical width M of the rotor cover 6 is about 10 mm, the diameter C on the rotor side is about 0.005 mm smaller than the diameter D on the opposite side.

A housing 8 houses the rotor 3, and has a substantially cylindrical inner surface 8a. The working chamber R is formed by the inner surface 8a of the housing, the outer surface of the rotor 3, and the vane 1.
form. 9 is a discharge hole formed in the housing 8; 10 is a discharge valve that covers this discharge hole; 11 is a cover for this discharge valve 10;
is fixed to the housing 8 with screws 12.

Reference numeral 13 denotes a discharge chamber housing that covers the discharge valve 10, and a bolt 15 is attached to the housing 8 via an elastic ring 14.
Fixed by Reference numeral 16 denotes a side plate disposed on the side surface of one end of the housing 8 via an O-ring 17, and this plate 16 has a discharge passage 18 communicating with the discharge chamber and a slat opening at a position facing the working chamber R. The opening port 19 is open. Further, a bearing 38 is driven into the plate 16, and the rotor cover 6 is rotatably supported by this bearing 38. Note that 22 is interposed between the discharge chamber housing 13 and the circumference of the discharge passage 18 of the side plate 16, and is used for sealing.
It's a ring.

An oil separator 20 is disposed on the side plate 16 via a gasket 21, and communicates with the discharge chamber 13a via the discharge passage 18. Inside this oil separator is a slugging valve 23.
The valve 23 is fixed to the side plate 16 with a spring 24 and a valve holder 25 with screws 26. The sludge valve 23 opens when the pressure inside the working chamber R becomes higher than the pressure inside the oil separator 20 by more than the set force of the spring 24, and prevents the inside of the working chamber R from becoming abnormally high pressure. Further, an oil supply passage 27 is formed in the valve holder 25, and this passage 27 communicates with the lower surface of the oil separator 20 via an oil supply pipe 28. Therefore, the lubricating oil accumulated in the lower part of the oil separator 20 is pushed up toward the oil supply passage 27 due to the pressure difference, and is supplied from the oil supply passage 27 to the one end surface 3a side of the rotor 3. Note that 29 is an oil filter and 30 is an oil check valve.

31 is a discharge pipe attached to the oil separator 20 with an O-ring 32 and a bolt 33. 34 is a blind plug for sealing this pipe 31, and 49 is a discharge service valve attached to the pipe 31. The refrigerant discharged from the discharge chamber 13 a to the oil separator 20 is discharged from the discharge pipe 31 after separating lubricating oil within the oil separator 20 .

35 is an O-ring 36 on the other end of the housing.
A bearing 37 is driven into this plate 35, and the shaft 5 is rotatably supported by this bearing 37. Further, this plate 35 has a suction hole 56 that connects a suction chamber and a working chamber R, which will be described later.

A front housing 39 is attached to the side plate 35 via a gasket 40, and has a suction chamber 41 and an oil storage chamber 42 formed therein (as shown in FIG. 3). 57 is a positioning pin for accurately attaching the gasket 40 to the side plate 35. A boss portion 43 is provided on the outer periphery of the front housing.
is formed, and an electromagnetic clutch (not shown) is attached to this boss portion. 44 is the front housing 39
47 is a suction service valve provided in the middle of this pipe 44, and 48 is a blind plug for sealing this pipe 44.

A shaft seal 50 seals between the shaft 5 and the front housing 39, and is composed of a carbon ring 51 that rotates integrally with the shaft 5, and a fixed ring 53 fixed to the housing 39 via an O-ring 52. Reference numeral 54 is a key for fixing a hub portion of an electromagnetic clutch (not shown) to the tip of the shaft 5.

Above front housing 39-gasket 40
- side plate 35 - housing 8 - side plate 16 - gasket 21 - oil separator 20 are integrally connected by through bolts 55.

Next, the operation of the compressor constructed as described above will be explained.

When an electromagnetic clutch (not shown) is engaged and the rotational force of the automobile engine is transmitted to the shaft 5, the shaft 5 is supported by bearings 37 and 38 and rotates within the housing 8. At a portion where the working chamber R expands in volume with this rotation, the refrigerant introduced into the suction chamber 41 from the evaporator of the refrigeration cycle is sucked into the working chamber R through the suction hole 56. The sucked refrigerant is compressed as the volume of the working chamber R decreases, and is discharged from the discharge hole 9 into the discharge chamber 13a.Then, after separating the lubricating oil in the oil separator 20, it is discharged from the discharge pipe 31 to the condenser side of the refrigeration cycle. Ru.

If the refrigerant remains in a liquefied state in the working chamber, such as during startup, the pressure in the working chamber R will become abnormally high if the engine continues to rotate. However, in this example, the sludging valve 23
, the abnormally high pressure within the working chamber R is released. Then, the liquid refrigerant that cannot escape from the sludge valve 23 remains in the working chamber R, and as a result, the pressure in the working chamber R increases, and a load that pushes open the vane groove 2 via the vane 1 is applied to the rotor 3. Even if this occurs, the rotor 3 of this example will not bite the inner surface 8a of the housing 8.

That is, as described above, the rotor of this example has a tapered shape in which the end surface 3a on one end side has a smaller diameter. A gap larger than the gap between the two is provided. Therefore, even if the vane groove 2 is pushed open by the vane 1, one end of the rotor 3 will not be pressed against the housing inner surface 8a.

Also, in this example compressor, oil separator 2
The lubricating oil collected in the lower portion is supplied to the end face of the rotor cover 6 from the suction passage 27, and then the lubricating oil is guided from the outer surface of the rotor to the bearing 37 side due to the pressure difference. Therefore, bearings 37, 38,
Sufficient suction is provided between the rotor 3 and the housing 8 and into the shaft seal.

Although the shaft seal 50 provides a sufficient seal, even if lubricating oil should leak from the shaft seal 50, the leaked oil will be stopped by the oil stopper 58. The stopped leaked oil is collected in the oil storage chamber 42 through a waste oil passage 59 formed in the front housing 39. Therefore, in the compressor of this example, even if lubricating oil should leak, the leaked oil will not scatter outside the compressor, and the area around the compressor will not be contaminated by the leaked oil.

In addition, in the above-mentioned embodiment, the vane 1 is located in the vane groove 2.
The vane 1 was penetrated through the vane 1 so that both ends 1c were in contact with the inner surface 8a of the housing, but if necessary, the vane 1
It is also possible to divide it into two parts so that only the tip on one end side contacts the inner surface 8a of the housing.

[Brief explanation of drawings]

FIG. 1 is a configuration diagram schematically showing the vane groove of a conventional compressor, FIG. 2 is an exploded perspective view of an embodiment of the compressor of the present invention, and FIG.
FIG. 4 is a front view of the rotor shown in the figure, and FIG. 4 is a sectional view showing the assembled state of the compressor shown in FIG. Figure 5 is a single part diagram of the vane. 1... Vane, 2... Vane groove, 3... Rotor, 5...
Shaft, 6... Rotor cover, 8... Housing.

Claims (1)

[Claims] 1. A shaft that rotates in response to a driving force, a cylindrical rotor that rotates integrally with the shaft, and a rotor that is formed over the entire length of the side surface of the rotor from an open end surface on one end side toward a closed end surface on the other end side of the rotor. a vane groove that diametrically penetrates the vane groove, a vane that is slidably disposed within the vane groove, a rotor cover that is disposed on an end surface of one end of the rotor that covers the open portion of the vane groove, and that houses the rotor. and a housing that forms a working chamber with the rotor outer circumferential vane, and the outer shape of the rotor is such that one end side having the vane groove open end is closer to the other end side having the vane groove closed end. A vane type compressor with a tapered shape that has a smaller diameter.