Rotary expansible chamber devices – Working member has planetary or planetating movement – With relatively movable partition member
Reexamination Certificate
2000-09-18
2002-06-25
Vrablik, John J. (Department: 3748)
Rotary expansible chamber devices
Working member has planetary or planetating movement
With relatively movable partition member
Reexamination Certificate
active
06409488
ABSTRACT:
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a rotary compressor to be used for the refrigerators, air conditioners, and the like.
2. Related Art of the Invention
Rotary compressors are much utilized for the refrigerators, air conditioners, and the like, because of their compact size and simple structure. The compression mechanism parts such as vane and roller which are the major constituting parts of the compressor are described in, for example, KAWAHIRA, “Sealed type refrigerator” (1993) P.14, FIG. 6.1.
Hereinafter, using
FIG. 6
, constitution and operation of the conventional rotary compressor are explained. The compression mechanism part in the sealed container comprises a crank shaft
101
having an eccentric part
109
, a bearing supporting the crank shaft
101
, a cylinder
102
, a vane
103
, and a roller
104
which eccentrically rotates in the cylinder
102
. The vane
103
having a cylindrical tip reciprocates in the vane slot
105
of the cylinder
102
, and its tip part is pressed to the outer peripheral surface of the roller
104
by the spring force by the spring
106
and the pressure difference between inside and outside of the cylinder
102
to slide in contact with the outer peripheral part of the roller
104
, thereby dividing the inner part of the cylinder
102
into the suction chamber
107
and the discharge chamber
108
. The part O is a center of the cylinder
102
and the crank shaft
101
. The crank shaft
101
has an eccentric part
109
centering on the point P which is eccentric by e from the center O. The crank shaft
101
rotates centering on O, and along with it the eccentric part
109
integral with the rank shaft rotates eccentrically. The roller
104
is engaged in the eccentric part
109
. Due to the rotation of the crank shaft
101
by the electric motor and the revolution of the roller
104
in the cylinder
102
, refrigerant gas is taken in from the suction port
110
and sent to the discharge port
111
while being compressed. The refrigerant gas from the discharge port
111
is sent to the refrigeration cycle side through the discharge valve
112
, and passed through the condenser, expansion valve, and evaporator to return to the suction port
110
of the compressor again.
In the above constitution, at the contact part between the roller
104
and the tip part of the vane
103
, an oil film has been formed by the oil which is mainly contained in the intake refrigerant and the oil which passes through the gap between the vane
103
and the vane slot
105
provided on the cylinder
102
or the gap between the end face of the roller
104
by the pressure difference.
The sealed container, bearing to support the crank shaft
101
, and electric motor are not illustrated.
However, according to the conventional constitution as above, as the tip part of the vane
103
has a cylindrical curved surface and the outer peripheral surface of the roller
104
is also cylindrical, the contact condition between the vane
103
and the roller
104
is equivalently the contact between the small cylinder and the large cylinder. Accordingly, the contact condition is a line contact condition wherein the contact area is smaller, and the load per unit area, i.e., contact stress, is larger, so that the contact sliding conditions between the vane
103
and the roller
104
become rigorous.
The number of autorotations of the roller
104
is also determined by the difference of the friction resistances between the inner peripheral surface and the eccentric part
109
and those between the outer peripheral surface of the roller
104
and the tip of the vane
103
and the like. The number of autorotations of the roller
104
is very unstable. In general, when the crank shaft
101
is operated at the revolution of 3500 rpm, the number of autorotations of the roller is about several scores to several hundreds rpm.
Because of the above, on the sliding surfaces of the tip of the vane
103
and the roller
104
the sliding speeds vary depending on conditions, and sliding movements become unstable.
Moreover, there is a problem that, in case of the use of the chlorine-free alternative refrigerant, e.g., R134a, remarkable lowering of lubrication occurs, and especially in case of the rotary compressor, wear is apt to occur between the outer periphery of the roller
104
and the tip of the vane where an oil film is less apt to be formed.
In order to settle the above points, for example, Japanese Patent Laid-open HEI 7-259767 discloses such construction that there are a horizontal hole
116
thrusting through the inside of the crank shaft
101
and its eccentric part
109
from the oil feed passage
115
to the outer diameter of the eccentric part
109
, an oil groove
117
provided on the outer diameter part of said eccentric part
109
in communication with the horizontal hole
116
, a groove
121
provided on the outer periphery of the roller
104
, a hole
120
thrusting through said outer peripheral groove
119
provided in parallel with said groove
119
at the deepest part of the groove
119
and a vane
103
is applied to the groove
119
.
According to said constitution, the contact between the roller
104
with the vane
103
becomes face contact and the autorotation of the roller
104
is also restricted, and stable sliding conditions can be realized. However, the oil supply to the contact part between the roller
104
and the vane
103
becomes intermittent because the hole
120
thrusting through from the inner diametrical part of the roller comes to be communicated with the side hole
116
provided to lead to the outer diametrical part of the eccentric part from the oil supply passage
115
only once in a turn. Therefore, no sufficient oil is supplied. Another drawback is that the oil to be supplied to the sliding part between the eccentric part
109
and the inner periphery of the roller
104
shows decrease.
In the first invention, in consideration of the points of the conventional compressors as shown in
FIG. 7
, an object is to provide a highly reliable, long life rotary compressor by reduced sliding load between the vane and the roller and supply of sufficient oil to the sliding part between the vane and the roller.
On the other hand, according to the constitution of the conventional compressor as in the above
FIG. 7
, the sliding conditions between the vane
103
and the roller
104
are improved, but the oil supply to the contact part between the roller
104
and the vane
103
involves drawbacks due to the complicated routes intervened by many relay points as described above, thus requiring complicated processing, having tendency to cause pooling of gases and difficulty of stabilized oil supply. Moreover, there has been no consideration given to the measures to be taken against the extremely large force applied to the inner peripheries of the eccentric part
109
and the roller
104
from the latter half part of the compression process.
The second invention is to settle the points of the conventional compressor of FIG.
7
. It aims at providing a more reliable, long life rotary compressor which is easily processed, does not give ill affect on other sliding part, assures stabilized oil supply, and permits reliable sliding and lubrication between the vane and the roller.
On the other hand, with respect to the groove part
119
of the conventional compressor shown in
FIG. 7
above, as shown in
FIG. 17
, in case of the contact sliding between the tip R part of the vane
103
and the groove
119
of the roller
103
according to the eccentric rotation of the roller
104
, if there are always or temporarily in the groove
119
the edge
122
on the suction chamber
107
side of the vane
103
and the edge
123
on the discharge chamber
108
side (the edge refers to the crossing part between the R part and the side surface), they have possibility to wear the groove part
119
. Also, due to the pressure difference between the suction chamber
107
side of the vane
103
and the discharge chamber
108
side, at the gr
Harada Terumaru
Hasegawa Hiroshi
Ikoma Mitsuhiro
Nishiwaki Fumitoshi
Shintaku Hidenobu
Matsushita Electric - Industrial Co., Ltd.
Smith , Gambrell & Russell, LLP
Vrablik John J.
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