Vane compressor

A rotor cover is disposed at one end surface of a rotor which has a ring-shaped locking ridge on the end surface thereof. The locking ridge has an outer peripheral surface fitted in a locking groove in the rotor cover. A holder is held against an inner peripheral surface of the locking ridge. With this arrangement, the diameter of the rotor is kept constant at all times, and so is the gap between the rotor and the housing, thus preventing scuffing of the rotor and the housing.

BACKGROUND OF THE INVENTION 
The present invention relates to a vane compressor, and more particularly 
to a vane compressor for use as a refrigerant compressor in an automobile 
air conditioning system. 
Vane compressors have a working chamber defined by the outer periphery of a 
rotor, side surfaces of vanes, the inner surface of a housing, and the 
inner surfaces of side plates. As the rotor rotates, the working chamber 
varies its volume to draw and discharge a refrigerant. Studies conducted 
by the inventor of conventional vane compressors have indicated that the 
rotor and the housing are subjected to much scuffing at one end surface of 
the rotor in operation. 
Such scuffing appears to be caused, according to the inventor, for the 
following reason: 
Any pool of liquid refrigerant left in the working chamber is compressed 
especially when the compressor is started. When this happens, as shown in 
FIG. 1 of the accompanying drawings, an unduly high pressure is exerted on 
vanes 1 which cause vane slots 2 to be widened. Since the vane slots 2 are 
cut out in the rotor 3 from one end surface 3a thereof, the vane slots 2 
are widened to a larger extent particularly at such rotor end surface 3a. 
Therefore, the rotor 3 is radially outwardly enlarged especially at the 
end surface 3a into pressing engagement with an inner surface 8a of the 
housing 8, with the result that the rotor 3 and the housing 8 are scuffed. 
SUMMARY OF THE INVENTION 
With the above conventional difficulty in view, it is an object of the 
present invention to provide a vane compressor designed to prevent a rotor 
from being radially enlarged to avoid scuffing of the rotor and the 
housing. 
According to the present invention, a rotor cover is disposed at one end 
surface of a rotor which has a ring-shaped locking ridge on the end 
surface thereof. The locking ridge has an outer peripheral surface fitted 
in a locking groove in the rotor cover. A holder is held against an inner 
peripheral surface of the locking ridge. With this arrangement, when the 
rotor is subjected to forces tending to spread the rotor radially 
outwardly, the outer peripheral surface of the locking ridge is pressed 
against the rotor cover to prevent the rotor from being spread radially 
outwardly. When forces are applied to the rotor in a direction to contract 
the rotor radially inwardly, the inner peripheral surface of the locking 
ridge is pressed against the holder to prevent the rotor from being 
deformed radially inwardly. The diameter of the rotor is therefore kept 
constant at all times, and so is the gap between the rotor and the 
housing, thus preventing scuffing of the rotor and the housing. 
The above and other objects, features and advantages of the present 
invention will become more apparent from the following description when 
taken in conjunction with the accompanying drawings in which preferred 
embodiments of the present invention are shown by way of illustrative 
example.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 
As shown in FIG. 2, a vane compressor according to the present invention 
includes a drive shaft 5 having an integral rotor 3. The drive shaft 5 and 
rotor 3 are made of steel (SCr9) and have a coeffcient of thermal 
expansion of about 12.times.10.sup.-6. The rotor 3 has cross-shaped radial 
vane slots 2 defined therein and extending from one end surface 3a fully 
across the width of the rotor 3. 
Vanes 1, each substantially C-shaped, are slidably disposed in the vane 
slots 2, and have a central portion 1a thinner than vane bodies 1b 
thereof. The vanes 1 are made of an aluminum alloy of high silicon, and 
have a coefficient of thermal expansion of about 18.times.10.sup.-6. The 
vanes 1 have distal ends 1c tapered into slightly thinner edges. The end 
surface 3a of the rotor 3 is covered with a rotor cover 6 fastened thereto 
by bolts 7 extending through the rotor cover 6 into threaded holes in the 
rotor 3. 
A holder 4 in the form of a stepped cylinder is interposed bewteen the 
rotor end surface 3a and the rotor cover 6. As shown in FIG. 3, the rotor 
end surface 3a has an integral ring-shaped locking ridge 3x with its outer 
peripheral surface engaging in a locking groove 6a defined in a side 
surface of the rotor cover 6 which faces the rotor 3. The holder 4 has a 
larger-diameter portion 4a having an outer peripheral surface pressed 
against the inner peripheral surface of the locking ridge 3x, and a 
smaller-diameter portion 4b pressed against an inner peripheral surface of 
the rotor cover 6. 
The components 1 through 7 referred to above are assembled as follows: The 
vanes 1 are axially inserted into the cross-shaped vane slots 2, and the 
holder 4 is press-fitted into the rotor 3 with the larger-diameter portion 
4a held against the inner peripheral surface of the locking ridge 3x. 
Then, the rotor cover 6 is placed on the rotor end surface 3a with the 
outer edge of the locking groove 6a fitting over the outer peripheral 
surface of the locking ridge 3x. The bolts 7 are threaded through the 
rotor cover 6 into the rotor end surface 3a, whereupon a rotor assembly is 
completed. 
The rotor 3 is accommodated in a housing 8 made of an iron-base material 
(FCD9) which is of the same kind as the material of the rotor 3. The 
housing 8 has a substantially cylindrical inner surface 8a. The inner 
surface 8a, the outer peripheral surface of the rotor 3, and the vanes 1 
jointly define a working chamber R. The housing 8 has a discharge port 9 
covered with a discharge valve 10 having a cover 11. The discharge valve 
10 and the cover 11 are fixed to the housing 8 by screws 12. 
The discharge valve 10 is covered with a discharge chamber housing 13 fixed 
to the housing 8 by bolts 15 with a resilient ring 14 interposed 
therebetween. A side plate 16 is attached to one end surface of the 
housing 8 with an O-ring 17 interposed therebetween, the side plate 16 
being made of cast iron (FCR9) which is of the same kind as the material 
of the rotor 3. The side plate 16 has defined therethrough a discharge 
passage 18 communicating with the discharge chamber 13a in the discharge 
chamber housing 13 and sludge ports 19 opening into the working chamber R. 
The side plate 16 accommodates a bearing 38 fitted therein and by which 
the rotor cover 6 is rotatably supported. A sealing O-ring 22 is 
interposed between the discharge chamber housing 13 and the side plate 16 
in surrounding relation to the discharge passage 18. 
An oil separator 20 is attached to the side plate 16 with a gasket 21 
interposed therebetween and communicates with the discharge chamber 13a 
via the discharge passage 18. Sludge valves 23 are disposed in the oil 
separator 20 and normally held in contact with the side plate 16 to close 
the sludge ports 19 by springs 24 and a valve holder 25 fastened by screws 
26 to the side plate 16. When the pressure in the working chamber R 
exceeds the pressure in the oil separtor 20 by a pressure setting given by 
the springs 24, the sludge valve 23 opens to prevent the interior of the 
working chamber R from being subjected to an unduly high pressure buildup. 
The valve holder 25 has an oil supply passageway 27 opening through an oil 
supply pipe 28 toward a lower surface of the oil separator 20. Lublicating 
oil collected in a lower portion of the oil separator 20 is pushed 
upwardly into the oil feed passageway 27 under a pressure difference, from 
which the lubricating oil is supplied to the rotor end surface 3a. 
Designated at 29 is an oil filter and 30 an oil check valve. 
A discharge pipe 31 is attached by a bolt 33 to the oil separator 30 with 
an O-ring 32 interposed therebetween. The pipe 31 is closed at one end by 
a blind plug 34. A discharge charging valve 49 is attached to the pipe 31. 
A refrigerant discharged from the discharge chamber 13a into the oil 
separator 20 is discharged through the discharge pipe 31 after lubricating 
oil has been separated from the refrigerant in the oil separator 20. 
A side plate 35 is attached to an opposite end surface of the housing 8 
with an O-ring 36 interposed therebetween, the side plate 35 being made of 
cast iron (FCR) which is of the same kind as the material of the rotor 3. 
The side plate 35 accommodates a bearing 37 fitted therein and by which 
the rotor shaft 5 is rotatably supported. The side plate 35 has an inlet 
hole 56 through which an inlet chamber (described later) and the working 
chamber R are connected. 
A front housing 39 is attached to the side plate 35 with a gasket 40 
interposed therebetween, and has an inlet chamber 41 and an oil reservoir 
42 (FIG. 4). The gasket 40 is attached accurately to the side plate 35 by 
positioning pins 57. The front housing 39 has on its outer surface a boss 
43 to which an electromagnetic clutch (not shown) is attached. An inlet 
pipe 44 is attached by a bolt 46 to the front housing 39 with an O-ring 46 
interposed therebetween. An inlet charging valve 47 is attached to an 
intermediate portion of the inlet pipe 44. The inlet pipe 44 is closed at 
one end by a blind plug 48. 
A shaft seal 50 provides a seal between the shaft 5 and the front housing 
39, and is composed of a carbon ring 51 rotatable with the shaft 5 and a 
fixed ring 53 secured through an O-ring 52 to the front housing 39. The 
hub of the electromagnetic clutch (not shown) is secured to the distal end 
of the shaft 5 by mean of a key 54 (FIG. 2). 
The front housing 39, the gasket 40, the side plate 35, the housing 8, the 
side plate 16, the gasket 21, and the oil separator 20 are coupled 
together as one assembly by means of through bolts 55. 
Operation of the vane compressor thus constructed is as follows: 
When the non-illustrated electromagnetic clutch is actuated to transmit 
rotative power from an automobile engine to the shaft 5, the shaft 5 that 
is rotatably supported by the bearings 37, 38 is rotated about its own 
axis in the housing 8. As the working chamber R is increased in volume as 
the shaft 5 rotates, the refrigerant introduced from an evaporator in a 
refrigerating cycle into the suction chamber 41 is drawn into the working 
chamber R via the inlet hole 56. The introduced refrigerant is 
progressively compressed as the volume of the working chamber R is 
reduced, and is discharged through the discharge hole 9 into the discharge 
chamber 13a. Then, lubricating oil is separated from the refrigerant in 
the oil separator 20, and thereafter the refrigerant is discharged via the 
discharge pipe 31 into a condenser in the refrigerating cycle. 
When the shaft 5 is rotated while the refrigerant is pooled as liquefied in 
the working chamber R as when the vane compressor is to be started, the 
pressure in the working chamber R becomes abnormally high. With the vane 
compressor according to the embodiment of the invention, the sludge valves 
23 open the ports 19 in the event of an excessive pressure buildup in the 
working chamber R, to allow the liquid refrigerant to escape via the ports 
19 into the oil separator 20. Therefore, an unduly high pressure buildup 
in the working chamber R is immediately eliminated and hence the vanes 1 
are prevented from suffering from damage which would otherwise be caused 
by such an undesirable pressure buildup. 
The pressure in the working chamber R still increases if the liquid 
refrigerant is not completely removed from the working chamber R. Even 
when a high pressure is imposed on the vanes 1, however, the vane slots 2 
are prevented from being spread since the rotor 3 is retained at the end 
surface 3a by the holder 4 against radially inward and outward 
displacement. Accordingly, the rotor 3 and the housing inner surface 8a 
are spaced by a constant gap at all times, and the housing inner surface 
8a will not be scuffed by the rotor 3. 
The rotor 3 and the holder 4 are pressed reliably against each other, and 
the holder 4 and the rotor cover 6 are also held reliably in intimate 
contact with each other. Therefore, the rotor 3 and the rotor cover 6 are 
positioned accurately with respect to each other, with the result that the 
shaft 5 and the rotor 3 are kept in accurate axial alignment with the 
rotor cover 6 and hence are rotatably supported properly by the bearings 
37, 38. 
Lubricating oil pooled in the lower portion of the oil separator 20 is fed 
through the inlet passageway 27 to the end surface of the rotor cover 6, 
from which the lubricating oil is led under a pressure difference to the 
bearing 37 via the outer peripheral surface of the rotor 3. The 
lubricatingil can therefore be supplied sufficiently to the bearings 37, 
38, the gap between the rotor 3 and the housing 8, and the shaft seal 50. 
The shaft seal 50 normally provides a sufficient seal during operation. If 
the lubricating oil leaks through the shaft seal 50, the oil leakage will 
be stopped by an oil stop 58 and guided into the oil reservoir 42 via a 
drain passage 59 defined in the front housing 39. In the event of any oil 
leakage, therefore, leaked oil will not be scattered out of the compressor 
and hence will not smear surroundings of the compressor. 
While in the foregoing embodiment each vane 1 extends through the vane 
slots 2 and has its opposite ends 1c contacting the housing inner surface 
8a, the vane 1 may be divided into two halves each having a distal end 
held in slidable contact with the housing inner surface 8a. 
The holder 4 may be of a disc shape as shown in FIG. 5. The holder 4 of 
FIG. 5 is held only at its outer peripheral surface in abutment against 
the inner peripheral surface of the locking ridge 3x, but is not fitted in 
the rotor cover 6. With this alternative arrangement, the rotor 3 and the 
rotor cover 6 are positioned relatively to each other by bringing the 
outer peripheral surface of the locking ridge 3x into intimate contact 
with the outer edge of the locking groove 6a. 
Although certain preferred embodiments have been shown and described, it 
should be understood that many changes and modifications may be made 
therein without departing from the scope of the appended claims.