JP3511680B2 - Rotary compressor - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a positive displacement machine, and more particularly to a rotary compressor suitable for use in a refrigeration cycle of a refrigerator or an air conditioner. 2. Description of the Related Art In a conventional rotary compressor, for example, as disclosed in Japanese Utility Model Laid-Open No. 3-129794, rollers and vanes are completely separated from each other and provided on a cylinder. The vane slot slidably incorporated in the vane slot is pressed against the outer periphery of the roller cylinder by linear contact with back pressure or spring force to maintain airtightness. [0003] In the above prior art,
Since the arc portion of the vane is pressed against the outer periphery of the roller cylinder by line contact, the local surface pressure is extremely high, and in severe operating conditions, wear and seizure occur, reducing the reliability of the compressor. was there. An object of the present invention is to prevent the vane tip and the outer periphery of the roller from sliding while in linear contact with each other in a rotary compressor and to adopt a sliding part of a sliding member which is required as a new part by adopting the structure. It is an object of the present invention to provide a highly reliable rotary compressor by lubricating and improving the lubricating state to eliminate severe sliding parts. In order to achieve the object of the present invention, according to the present invention, a vane and a roller are arranged such that two parallel planes of the vane and a central axis of a cylindrical outer peripheral surface of the roller are mutually aligned. The vanes are joined or integrally molded in a parallel state, and the vane is further swung around one axis on the cylinder parallel to the central axis of the cylindrical inner peripheral surface of the cylinder and reciprocated in a plane including the one axis. The space provided in the direction opposite to the cylindrical inner peripheral surface communicating with the cylindrical hole of the cylinder is sealed with a plurality of side plates at both ends, so that And an opening provided in the cylinder so as to communicate with the suction passage, and the opening and the space opening communicate with each other through a groove formed in the cylinder end surface. The side play A vane that communicates with the space and the suction passage of the refrigerant by a path formed by covering with a sheet to reduce the pressure in the space, and penetrates the inside of the vane from the inner periphery of the roller to abut the sliding member flat portion. An oil supply path communicating with the plane portion is provided, and an oil supply path communicating from the plane portion of the sliding member abutting on the opening portion of the vane plane portion of the oil supply path to the outer peripheral cylindrical surface portion is further provided. An oil supply groove is provided in any circumferential direction of the oil supply path which penetrates the inside and abuts the roller inner peripheral opening. In the structure of the means for solving the above problems, when the center of the roller makes a revolving motion by the driving mechanism,
The roller can swing by a small amount around its central axis to orient the combined or integrally formed vane in the direction of one axis on the cylinder parallel to the central axis of the cylindrical inner peripheral surface of the cylinder. At this time, the vane repeats forward and backward movements while swinging a small amount around one axis on the cylinder. By using a structure in which the cylinder supports the vane so that the vane can swing and move forward and backward, the space between the roller and the cylinder can be partitioned by the vane even if the vane and the roller are combined or integrally formed. Thus, it is possible to configure a rotary compressor in which the vanes and the rollers do not slide at all and wear does not occur between them. Further, when the vane and the roller are combined or formed integrally, the vane portion is supported by a cylinder via a sliding member because the integral member performs a swinging motion. When the pressure acting on the back of the vane is high as in the prior art, the sliding member is pressed against the compression chamber by the pressure difference between the high pressure chamber and the compression chamber inside the cylinder, and the sliding state becomes severe. However, in the structure of the means for solving this problem, the pressure acting on the back surface of the vane is low, so that the sliding member is pressed against the back pressure chamber side, but the sliding pressure is reduced because the differential pressure is reduced. The force with which the member is pressed can be reduced. Furthermore,
The oil supplied to the inner periphery of the roller by the centrifugal force of the crankshaft passes through the oil supply path provided inside the vane to the flat portion of the sliding member, or further, to the outer peripheral cylindrical surface of the sliding member through the oil supply path provided in the sliding member. The lubrication can be reliably performed, the sliding conditions can be relaxed, and the reliability can be improved. FIG. 1 to FIG. 1 show a first embodiment of the present invention.
1 will be described. 1 is a side sectional view of a rotary compressor according to an embodiment of the present invention, FIG. 2 is a sectional view taken along a line II in FIG. 1, FIG. 3 is an explanatory diagram of a back pressure chamber sealing method in the embodiment of the present invention,
FIG. 4 is an explanatory view of a communication path connecting the suction passage and the back pressure chamber in the embodiment of the present invention, and FIG. 5 is an oil supply path connecting the roller inner periphery of the roller and the vane integral member and the vane flat portion in the embodiment of the present invention. FIG. 6 is an explanatory view of an example of an oil supply path connecting the flat portion of the sliding member and the outer peripheral cylindrical surface in the embodiment of the present invention. FIG. 7 is an oil supply groove on the outer periphery of the crank pin portion in the embodiment of the present invention. , FIG. 8 is an explanatory view of an oil supply path in the embodiment of the present invention, FIG. 9 is an explanatory view of the movement of each part in FIG. 2 when a compressor driving motor is rotated by 90 °, and FIG. Is an enlarged view of a pump portion in FIG. 1, and FIG. 11 is a sectional view of a pump portion of a conventional rotary compressor. FIG. 12 is an enlarged view of a pump portion according to the second embodiment of the present invention. In the first embodiment of the present invention shown in FIGS. 1 to 10, a cylindrical hole 1a is formed in the center of a cylinder 1, and a first plate member is formed so as to close both ends thereof. 2 and the second plate member 3 are fixed by bolts 4. At this time, the holes 2 formed in the bosses 2a, 3a at the center of the first plate member 2 and the second plate member 3 are formed.
The central axes of b and 3b are fixed so as to be coaxial with the central axis of the cylindrical hole 1a of the cylinder 1. The outer peripheral portion of the cylinder 1 to which the first plate member 2 and the second plate member 3 are fixed is fixed to the chamber 5. The stator 5 of the compressor driving motor is fixed to the chamber 5. A crankshaft 7 is supported by bearings in the holes 2b and 3b. An outer periphery of a rotor portion 8 fixed to an end portion of the crankshaft 7 is incorporated into an inner periphery of the stator portion 6 with a small gap, and a compressor is provided. Motor is formed.
The crankshaft 7 is formed with a cylindrical crankpin portion 7a eccentric to the center axis of the crankshaft 7 at a position corresponding to the cylindrical hole 1a of the cylinder 1. A vane 10 is integrally fixed to one portion of the outer periphery of the roller 9 by welding or the like. At this time, two parallel planes of the vane 10 are parallel to the central axis of the roller 9. Fixed to. Outside the cylindrical inner peripheral surface 1a of the cylinder 1, a cylindrical hole 1b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a is formed. Each side is a cylindrical inner peripheral surface 1a
And another space 11 provided outside the cylindrical hole portion 1b. The vane 10 is inserted into the cylindrical hole portion 1b and the space 11, and between the vane 10 and the cylindrical hole portion 1b, a flat portion slidably abutting on the flat portion of the vane 10 and the cylinder of the cylindrical hole portion 1b. A sliding member 12 having a cylindrical outer peripheral surface slidably in contact with the inner peripheral surface of the shape is incorporated with the vane 10 interposed therebetween, and as a result, the vane 10 has a cylindrical hole 1b.
Are supported by the cylinder 1 so as to be able to move back and forth in the direction of the central axis and swinging movement around the central axis. The tip of the vane 10 on the opposite side of the joint with the roller 9 moves in the space 11 and does not interfere with the cylinder 1. [0011] As shown in FIG.
0 and a hole passing through the vane 10
A refueling passage 1 formed by providing a hole that opens in a flat surface portion and closing the opening at the tip end of the vane 10 of the through hole with a sealing member 19.
0a is provided. In addition, the sliding member 12 includes
As shown in FIG. 5, an oil supply path 12a is provided which communicates from the plane part of the sliding member 12 which comes into contact with the opening of the vane plane part of the oil supply path 10a of the vane 10 to the outer peripheral cylindrical surface part.
Further, as shown in FIG.
An oil supply groove 7c is provided in a circumferential direction of an outer peripheral portion of the oil supply path 10a which is in contact with the inner peripheral opening of the roller. The opening of both ends of the space 11 is closed by a flange 2c of the first plate member 2 and a flange 3c of the second plate member 3. Further, the space 11 has a cylinder end face opening of a through hole 1d provided in the cylinder 1 so as to communicate with the suction passage 1c, and a groove formed in the cylinder end face with the opening and the cylinder end face opening of the space 11. The opening and the groove 1e communicate with each other by 1e and are covered with the flange 3c of the second plate member. Therefore, space 1
The pressure in 1 is the suction pressure. With the above configuration, when the rotor section 8 of the compressor driving motor rotates, the crankshaft 7 fixed thereto also rotates. Accordingly, the crankpin portion 7a formed eccentrically to the crankshaft 7 also rotates, and the roller 9 is given a revolving motion. FIG. 9 is a view showing the movement of the roller 9 and the vane 10 integrated with the roller 9 when the rotor unit 8 of the compressor driving motor rotates by 90 °. 9 rotates around the center of the crankpin portion 7a of the crankshaft 7 by a small angle around the center of the crankpin portion 7a of the crankshaft 7 so that it always faces the center line direction of the cylindrical hole portion 1b of the cylinder. I do. Vane 10 is the cylindrical hole 1 of cylinder 1
b moves forward and backward in the direction of the central axis and swings around the central axis, but the seal of the gap between the vane 10 and the cylindrical hole 1b of the cylinder 1 is maintained by inserting the sliding member 12. . Therefore, a compression chamber, which is a closed space, is formed by the cylinder 1, the roller 9, the vane 10, the first plate member 2, and the second plate member 3, and the rotation of the rotor unit 8 of the compressor driving motor causes the compression chamber to rotate as shown in FIG. The increase and decrease of the volume are repeated as shown in FIG. A first side chamber 13 and a second side chamber 14 are welded to openings at both ends of the chamber 5,
A closed container is formed as a whole. The working gas flows into the compressor through the suction port 15, is drawn through the suction passage 1 c formed in the cylinder 1, is compressed in the compression chamber by increasing or decreasing the volume of the compression chamber, and is formed in the second plate member 3. The discharge port (not shown) is discharged through the discharge valve 16 and the discharge valve retainer 17. Thereafter, the fluid flows out of the compressor through a discharge port 18 provided in the second side chamber 14 through the motor chamber. In this embodiment, since the roller 9 and the vane 10 are integrated, the roller 20 and the vane 21 are separated from the roller 20 and the vane 21 of the conventional structure shown in FIG. This eliminates the need for the preload spring 22 and the back pressure of the vane, which have been necessary to prevent the occurrence of the pressure. Further, in the structure shown in FIG. 11, the contact portion between the tip of the vane 21 and the outer periphery of the roller 20 and the contact portion between the vane 21 and the slit portion of the cylinder 23 are in linear contact or close contact therewith. While a local concentrated load acts on the pressure of the compressed gas directly acting on the cylinder 21, the pressure of the compressed gas directly acting on the vane 10 in the structure of the present embodiment is controlled by the cylinder 1 of the cylinder 1 via the sliding member 12. The hole 1b and the crankpin 7a of the crankshaft are supported, and all can be supported by surface contact. That is, the sliding surface pressure of the sliding portion around the vane 10 can be reduced as compared with the conventional structure, and the durability can be improved. Next, when the pressure inside the space 11 is a high pressure as in the conventional structure, the sliding member 12 is pressed against the compression chamber by the pressure difference between the high pressure and the compression chamber in the cylinder 1, and the sliding member 12 is slid. Becomes harsh. However, in the structure of the embodiment of the present invention, since the pressure inside the space 11 is low,
Is pressed against the space 11, but the pressure difference is smaller than when the space 11 is at a high pressure, and the force with which the sliding member 12 is pressed can be reduced. Next, in the structure of this embodiment, the crankpin portion 7a is formed by the centrifugal force of the crankshaft 7 from the oil supply hole 7b of the crankshaft 7 through the oil supply path shown in FIG.
The oil supplied to the sliding member 12 is supplied to the sliding member 12 by a differential pressure between the space 11 and the compression chamber, from an oil supply groove 7c provided in the circumferential direction of the outer periphery of the crank pin portion 7a, through an oil supply path 10a provided in the vane 10. Oil can be reliably supplied to the flat surface portion and further to the outer peripheral cylindrical surface of the sliding member 12 through an oil supply path 12a provided in the sliding member 12. Further, the sliding member 1
The flat part and the outer peripheral cylindrical surface of No. 2 are respectively provided with oil supply grooves 12b, 1
2c, so that the supplied oil can be supplied to the entire flat surface or the entire outer peripheral cylindrical surface. That is, the sliding conditions of each sliding surface of the sliding member 12 can be relaxed to improve reliability. Further, in the second embodiment of the present invention shown in FIG. 12, even if the position of the roller inner peripheral opening of the oil supply path 10a of the vane 10 is opened to a part which does not slide with the crank pin part 7a, An effect equivalent to the effect can be obtained. According to the present invention, a rotary compressor having high durability can be provided.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view of a rotary compressor according to a first embodiment of the present invention. FIG. 2 is a sectional view taken along the line II in FIG. FIG. 3 is an explanatory diagram of a back pressure chamber sealing method according to the first embodiment of the present invention. FIG. 4 is an explanatory diagram of a communication path connecting a suction passage and a back pressure chamber in the first embodiment of the present invention. FIG. 5 is an explanatory diagram of an oil supply path connecting an inner periphery of a roller and a vane flat portion of an integrated member of the roller and the vane according to the first embodiment of the present invention. FIG. 6 is an explanatory diagram of an oil supply path connecting the flat portion of the sliding member and the outer peripheral cylindrical surface in the first embodiment of the present invention. FIG. 7 is an explanatory view of an oil supply groove on the outer periphery of a crank pin portion in the first embodiment of the present invention. FIG. 8 is an explanatory diagram of a refueling path in the first embodiment of the present invention. FIG. 9 is an explanatory view of the movement of each component in FIG. 2 when the motor for driving the compressor is rotated by 90 °. FIG. 10 is an enlarged view of a pump portion in FIG. 1; FIG. 11 is a sectional view of a pump portion of a conventional rotary compressor. FIG. 12 is an enlarged view of a pump portion according to a second embodiment of the present invention. [Description of References] 1 ... cylinder, 1a ... cylindrical hole, 2 ... first plate member, 2a, 3a ... boss, 2b ... hole, 2c, 3c ...
Flange, 3 ... second plate member, 4 ... bolt, 5 ... chamber, 6 ... motor stator, 7 ... crankshaft,
7a: crank pin portion, 8: rotor portion of motor, 9: roller, 10: vane, 11: space, 13: first side chamber, 14: second side chamber, 16: discharge valve, 1
7: Discharge valve holder, 18: Discharge port, 19: Sealing member.

────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-7-158574 (JP, A) JP-A-7-174088 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04C 18/30-18/336 F04C 18/356 F04C 29/02 311

Claims (1)

(57) and [Claims 1 cylinder, and a plurality of side plates for closing both end portions of the inner peripheral surface of the cylinder, in a surrounded by said cylinder and said side plate space a roller cylindrical outer peripheral surface thereof to revolve while maintaining always a small gap between the cylindrical inner peripheral surface of said cylinder, a torque crankshafts give revolve the roller, the cylindrical of the cylinder A vane that further partitions an enclosed space surrounded by an inner peripheral surface, the cylindrical outer peripheral surface of the roller, and the plurality of side plates into a plurality of enclosed spaces, wherein the vane and the roller are provided by the vane. in a state where two parallel planes and the center axis of the cylindrical outer peripheral surface of the roller are parallel to each other, a member coupled or integrally formed, wherein the cylindrical inner periphery to the outside of the cylindrical inner peripheral surface of the cylinder Said cylindrical hole said base <br/> over emissions inserted into a cylindrical hole having a central axis parallel to the center axis and the flat portion slidably in contact with the flat portion of the vane between the cylindrical hole of A sliding member having a cylindrical outer peripheral surface slidably in contact with the cylindrical inner peripheral surface of the portion.
In a rotary compressor including, Russia Tari compressor provided with a fuel supply path for communicating the inner periphery and the sliding member flat portion abutting portions of the flat portion of the vane of the rollers inside the vane.