Rotary expansible chamber devices – Working chamber surface expressed mathematically
Patent
1983-11-01
1985-08-20
Vrablik, John J.
Rotary expansible chamber devices
Working chamber surface expressed mathematically
418259, F04C 1800, F04C 2908
Patent
active
045361410
DESCRIPTION:
BRIEF SUMMARY
FIELD OF THE INVENTION
This invention relates to a rotary compressor for car air conditioning which has, for example, vanes and a wide ranging rotational speed.
BACKGROUND ART
Generally, a sliding vane type compressor, as shown in FIG. 1, comprises a cylinder 1 having therein a cylindrical space, side walls (not shown in FIG. 1) being fixed to both sides of the cylinder 1, and sealing blade chambers 2a and 2b being defined on opposite sides of the inner space in the cylinder 1, a rotor 3 disposed at the center thereof, vanes 5 being slidably engageable with grooves 4 provided in the rotor 3, suction bores 6a and 6b being formed in the cylinder 1, discharge bores 7a and 7b being formed in the same, communication conduits 8a and 8b communicating with the blade chambers 2a and 2b and the bore 6a and 6b being formed in the cylinder 1, and set screws 9a and 9b being provided at the suction side and those 10a and 10b being provided at the discharge side.
The vanes 5 project outwardly by a centrifugal force as the rotor 3 rotates, so that the outermost ends of vanes 5 slidably move along the inner periphery of cylinder 1, thereby prevent leakage of gas from the compressor.
FIG. 2 is a sectional side view of the compressor, in which reference numeral 11 designates a front plate reference numeral 12 designates a rear plate, reference numeral 13 designates a front casing, reference numeral 14 designates a rotary shaft, reference numeral 15 designates a shell, reference numeral 16 designates an annular suction conduit formed between the front casing 13 and the front plate 11, reference numeral 17 designates a suction piping joint, reference numeral 18 designates a suction conduit shown in broken line, reference 19 designates a disc for a clutch means, and reference numeral 20 designates a pulley for the clutch means.
The compressor, as shown in FIG. 1, having the cylinder 1 with an inner surface non-circular in section, requires a plurality of pairs of suction bores and discharge bores.
The inner surface of cylinder 1 being about elliptic in section, the compressor discharges a refrigerant compressed in the right-hand and left-hand blade chambers 2a and 2b through two discharge bores 7a and 7b into a common space 21 formed of cylinder 1 and shell 15.
Supply of the sucked refrigerant into two blade chambers 2a and 2b is separate from the discharge side and cut off therefrom by use of a construction shown in FIG. 2.
In detail, between the front plate 11 and the front casing 13 is formed the annular suction conduit 16 communicating in common with two suction bores 6a and 6b and the piping joint 17 provided at the front casing 13 connects the conduit 16 with an external refrigerant supply source (an exit of an evaporator).
Such a construction need only provide such one suction and piping joint even in a multilobe type compressor having two or more cylinder chambers.
Such a sliding vane type rotary compressor can be small-sized and simple in construction rather than the reciprocating compressor which is complex in construction and of many parts, thereby having recently been used for the car cooler compressor. The rotary compressor, however, has the following problems in comparison with the reciprocating compressor.
In a case of a car cooler (air conditioner), a driving force is transmitted from an engine to the pulley 20 at the clutch means through a belt to drive rotary shaft 14 of the compressor. Hence, when the sliding vane type compressor is used, its refrigerating capacity rises about linearly in proportion to the rate of rotation of the car engine.
On the other hand, in the case of using the reciprocating compressor, the follow-up property (response) of a suction valve becomes poor during high speed rotation and the compressed gas cannot be fully sucked into the cylinder. As a result, the refrigerating capacity leads to saturation during high speed driving. In brief, while the reciprocating compressor automatically suppresses the refrigerating capacity during the high speed driving, the rotary one does not do so
REFERENCES:
patent: 3565558 (1971-02-01), Tobacman
Matsushita Electric - Industrial Co., Ltd.
Vrablik John J.
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