JPH07208366A - Rotary compressor - Google Patents

Abstract

PURPOSE:To prevent an end of vane from sliding with an outer periphery of a roller while being in linear contact and reduce torque fluctuation by supporting the vane by means of a cylinder such that oscillations around one axis on the cylinder parallel to the center axis of a cylindrical inner peripheral surface of the cylinder and reciprocation in the plane including one axis are enabled. CONSTITUTION:When centers of rollers 11, 12 are revolved by a driving mechanism, the vanes 13, 14 connected or integrated with around the centers of the rollers with minute oscillations can be arranged in an axis on a cylinder parallel to the center axes of cylinders 1, 2. The cylinders 1, 2 support the vanes 13, 14 such that the vanes 13, 14 can be oscillated and reciprocated. A space between the rollers and the cylinders can be partitioned by the vanes 13, 14. A rotary compressor in which the vanes are not slid with the rollers and abrasion is not generated therebetween can be formed, and reliability is improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary positive displacement machine, and more particularly to a rotary compressor suitable for use in a refrigeration cycle of a refrigerator or an air conditioner.

[0002]

2. Description of the Related Art In a conventional rotary compressor, for example, as disclosed in Japanese Utility Model Laid-Open No. 3-129794, a roller and a vane are completely separate, and a vane slot provided in a cylinder. The tip arc portion of the vane slidably mounted on the roller was pressed against the outer circumference of the roller cylinder by line contact by back pressure or spring force to maintain airtightness.

[0003]

SUMMARY OF THE INVENTION In the above conventional technique,
Since the arc portion of the tip of the vane is pressed against the outer circumference of the cylinder of the roller by line contact, the local surface pressure is very high, and there is a problem that abrasion and seizure occur in severe operating conditions, reducing the reliability of the compressor. there were. Further, the rotary compressor has a problem that the torque fluctuation is large and the vibration is large as compared with the scroll compressor.

An object of the present invention is to provide a rotary compressor of high reliability and low vibration, which prevents the vane tip and the roller outer periphery from sliding in line contact with each other in the rotary compressor and reduces torque fluctuation. Especially.

[0005]

An object of the present invention is to integrally or integrally form a vane and a roller with two parallel planes of the vane and a central axis of a cylindrical outer peripheral surface of the roller being parallel to each other. In addition, the vane is supported by the cylinder so that the vane can swing about one axis on the cylinder parallel to the central axis of the cylindrical inner peripheral surface of the cylinder and can move back and forth in a plane including the one axis. When the number of cylinders is n and the number of cylinders is n, the phase of the compression chamber in each cylinder is approximately (360 / n). Achieved by shifting each time.

[0006]

According to the structure of the means for solving the above problems, when the center of the roller orbits by the drive mechanism,
The roller can swing a small amount around its central axis to direct the vanes integrally coupled or integrally formed to 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 the forward / backward movement while swinging a minute amount around the axis of the cylinder. By adopting a structure in which the cylinder supports the vane so that the swinging motion and the reciprocating motion of the vane are possible, even if the vane and the roller are combined or integrally formed, the space between the roller and the cylinder is partitioned by the vane. This makes it possible to construct a rotary compressor in which the vanes and rollers do not slide at all and wear does not occur between them, and reliability can be improved.

Further, when the vane and the roller are connected or integrally formed, the swinging motion of the integrated member, particularly torque fluctuation due to the inertial force occurs due to the moment of inertia of the roller portion. To solve this problem. In the structure of the means of (1), there are multiple cylinders (n cylinders), and the phase thereof is (360 /
n) By shifting by degrees, the torque fluctuation generated in another cylinder due to the compression work and the torque fluctuation generated due to the inertial force can be canceled each other to reduce the overall torque fluctuation width. It is possible to reduce vibration more than it becomes.

[0008]

Embodiments of the present invention will be described below with reference to FIGS. 1 is a side sectional view of a two-cylinder rotary compressor according to an embodiment of the present invention, FIG. 2 is a sectional view taken along the line II of FIG.
FIG. 3 is a diagram for explaining the movement of each component in FIG. 2 when the motor for driving the compressor is rotated by 90 °, and FIG. 4 is a torque fluctuation of the two-cylinder rotary compressor shown as an embodiment of the present invention. 5 is a sectional view of a pump portion of a conventional rotary compressor, and FIG. 6 is a diagram showing torque fluctuations in a single cylinder and two cylinders of the conventional rotary compressor.

In the two-cylinder rotary compressor according to the embodiment of the present invention shown in FIGS. 1 to 4, holes 1a and 2a are formed in the central portions of the first cylinder 1 and the second cylinder 2, respectively. The first plate member 3, the second plate member 4, and the third plate member 5 are fixed by bolts 6 so that both ends thereof are closed. At that time, the boss portions 3a, 5a in the central portions of the first plate member 3 and the third plate member 5
Each of the center axes of the hole portions 3b and 5b formed in the above is fixed so as to be coaxial with the common center axis of the hole portions 1a and 2a of the first cylinder 1 and the second cylinder 2. The outer periphery of the first plate member 3, to which the third plate member 5, the first cylinder 1, the second plate member 4, and the second cylinder 2 are fixed, is fixed to the chamber 7. A stator portion 8 of a compressor driving motor is fixed to the chamber 7, and an inner circumference of the stator portion 8 is fitted with a rotor portion 9 having a minute gap from the outer circumference of the stator portion 8. Forming a motor for the. The crankshaft 10 is provided in the holes 3b and 5b.
Is supported by a bearing, and a rotor portion 9 is fixed to an end portion of the crankshaft 10. Crankshaft 10
Are the holes 1a, 2a of the first cylinder 1 and the second cylinder 2.
Cylindrical crank pin portions 10a and 10b, which are eccentric to the central axis of the crankshaft 10, are formed at positions corresponding to the inside by shifting the eccentric direction by 180 °. In the holes 1a and 2a of the first cylinder 1 and the second cylinder 2, cylindrical rollers 11 and 12 are respectively provided in the crank pin portions 10a and 1a.
It is rotatably supported and incorporated by 0b.

The vanes 13 and 14 are integrally fixed to one place on the outer circumferences of the rollers 11 and 12 by a method such as welding. At that time, the two parallel planes of the vanes 13 and 14 are respectively fixed to the rollers 11. , 12 are fixed so as to be parallel to the central axis of the cylindrical surface. The cylindrical inner peripheral surface 1 is provided outside the cylindrical inner peripheral surfaces 1a and 2a of the first cylinder 1 and the second cylinder 2.
holes 1b and 2b having central axes parallel to the central axes of a and 2a
Are formed, and the space at the center of the cylinder and the hole 1 are respectively defined on the cylinder center side of the holes 1b and 2b and on the opposite side thereof.
It communicates with the other spaces 15 and 16 provided outside b and 2b. Although the vanes 13 and 14 are inserted into the holes 1b and 2b, respectively, the vane 13 and the holes 1b and 1
4 and the hole 2b between the flat portion of the vane 13 or 14 slidably abutting against the flat portion of the vane 13 or 14 and the hole 1b or 2
A sliding member 17 having a cylindrical surface that slidably abuts the cylindrical inner peripheral surface of b is incorporated with the vanes 13 and 14 sandwiched between them, and as a result, the vanes 13 and 14 are inserted into the holes 1b and 2b. It is supported by the first cylinder 1 and the second cylinder 2 so as to be able to move back and forth within a plane including the central axis and swinging around the central axis. The tip ends of the vanes 13 and 14 on the side opposite to the joints with the rollers 11 and 12 move in the spaces 15 and 16, respectively, and do not interfere with the first cylinder 1 and the second cylinder 2.

When the rotor portion 9 of the compressor driving motor rotates, the crankshaft 10 fixed to this also rotates. Along with this, the crank pin portions 10a and 10b formed eccentrically on the crankshaft 10 also rotate, and the rollers 11 and 12 are revolved. FIG. 3 is a diagram showing the movement of the roller 11 and the vane 13 integrated with the rotor 11 when the rotor portion 9 of the compressor driving motor is rotated by 90 °. The roller 11 is integrated with the vane 13. 3 makes a revolving motion while swinging around the center of the crank pin 10a of the crankshaft 10 by a slight angle in the plane of FIG. 3 so that it always faces the center of the hole 1b of the cylinder. The vane 13 performs an advancing / retreating motion in a plane including the central axis of the hole 1b of the first cylinder 1 and an oscillating motion about the central axis, but there is a gap between the vane 13 and the hole 1b of the first cylinder 1. The seal is maintained by inserting the sliding member 17. Therefore, the first cylinder 1, the roller 1
1, the vane 13, the first plate member 3, and the second plate member 4 form a compression chamber that is a closed space, and the volume thereof increases and decreases as shown in FIG. 3 as the rotor portion 9 of the compressor driving motor rotates. repeat. Similarly, in the second cylinder 2, the crank pin portion 10b is 180
The eccentricity is deviated and the hole 2b of the second cylinder 2
Is formed in the same direction as the hole portion 1b of the first cylinder 1, so that the volume is repeatedly increased and decreased with the phase shifted by 180 degrees from the inside of the first cylinder 1.

A first side chamber 18 and a second side chamber 19 are welded to the openings at both ends of the chamber 7,
A closed container is formed as a whole. The working gas flows into the compressor through the suction port 20 shown in FIG. 2, and the suction passage 3c formed in the first plate member 3, the suction passage 1c formed in the first cylinder 1, the second plate member 4, After passing through a suction passage (not shown) formed in the two cylinders 2, the suction hole 1d of the first cylinder 1 and the second cylinder 2
After being sucked into the first cylinder 1 or the second cylinder 2 through a suction hole (not shown), the volume of the compression chamber is increased and decreased to be compressed in the compression chamber and the first plate member 3 or the third plate member 5 is compressed. The formed discharge port (not shown) passes through the discharge valves 21 and 22, discharge valve retainers 23 and 24, and is discharged. After that, it passes through the motor chamber and flows out of the compressor from the discharge port 25 provided in the second side chamber 19.

In this embodiment, since the roller 11 and the vane 13 and the roller 12 and the vane 14 are integrated, the roller 26 and the vane 27 of the conventional structure example shown in FIG. 6 are different from the separate structure. There is an effect that the preload spring 28 and the back pressure, which are required to prevent the roller and the vane from coming off, become unnecessary. Further, in the structure of FIG.
Since the contact portion between the tip end and the outer periphery of the roller 26 and the contact portion between the vane 27 and the slit portion of the cylinder 29 have a line contact or a contact form close thereto, the preload spring 28 and the back pressure and the pressure of the compressed gas directly acting on the vane 27. Due to this, a localized concentrated load acts, whereas in the structure of the present embodiment, the pressure of the compressed gas that directly acts on the vanes 13 and 14 is the sliding member 1.
Holes 1 of the first cylinder 1 and the second cylinder 2 through
b, 2b and the crankpin portion 10a of the crankshaft,
It will be supported by 10b, and all can be supported by surface contact. That is, the sliding surface pressure of the sliding portion around the vanes 13 and 14 can be greatly reduced as compared with the conventional structure, and the durability can be improved.

Further, in this embodiment, the spaces 15 and 16 in which the tips of the vanes 13 and 14 provided on the cylinder move.
Has a high pressure because it communicates with the inside of the high-pressure closed container surrounded by the chamber 7, the first side chamber 18, and the second side chamber 19, and the mist-like lubricating oil exists. As a result, there is a pressure gradient between the spaces 15 and 16 and the compression chamber, and between the cylindrical surface of the sliding member 17 and the holes 1b and 2b of the cylinder, and between the flat surface of the sliding member 17 and the vane 1.
A flow of the refrigerant is generated between the plane portions 3 and 14, and the lubricating oil is supplied by the flow, so that the portion can be lubricated.
It should be noted that this effect can be obtained similarly even in the case of a single cylinder.

On the other hand, as a known technique, in the conventional rotary compressor, the number of cylinders is set to be plural (n cylinders) and the phase of each cylinder is shifted by (360 / n) degrees to change the torque fluctuation range. It is known that vibration can be reduced by reducing the size. For example, according to the diagram showing the torque fluctuation associated with the compression work in the single cylinder and the two cylinders of the conventional rotary compressor shown in FIG. 6, the torque fluctuation line of the single cylinder is shown in FIG.
6B, which is the torque fluctuation line of the two cylinders, the two torque fluctuation diagrams of the single cylinder that are 180 (360 / n) degrees out of phase cancel each other's peaks and troughs. It can be seen that the amplitude of the composite wave is smaller than in the case of a single cylinder. On the other hand, in this embodiment, the roller 11 and the vane 1
3, or the torque fluctuation of the inertial force generated by the rocking motion of the member in which the roller 12 and the vane 14 are integrated can further cancel the torque fluctuation due to the compression work, and is more than that of the conventional multi-cylinder type. Furthermore, low vibration can be realized. That is, FIG. 4A is a diagram showing torque fluctuations in the case of the two-cylinder shown in FIG. 4 as one embodiment of the present invention, which is a torque fluctuation line accompanying compression work that appears as in the conventional mechanism and FIG. Depending on the structure, the roller 11 and the vane 13 or the roller 1 may be newly added.
4 and FIG. 4B, which is the torque fluctuation line due to the inertial force generated by the swing motion of the member in which the vane 14 and the vane 14 are integrated, have a relationship in which peaks and valleys and valleys and peaks overlap. as a result,
By canceling the torque fluctuations with each other, the fluctuation width in C of FIG. 4 which is the combined torque fluctuation line becomes smaller than the fluctuation width of B of FIG. 6 which is the torque fluctuation line of the two-cylinder type of the conventional mechanism. Vibration can be reduced.

In particular, according to the present embodiment, the inertia generated when the roller 11 and the vane 13, or the integrated member of the roller 12 and the vane 14 is swung, even during high-speed rotation where the vibration generally increases. When the torque fluctuation due to the force is further increased, the effect of canceling the torque fluctuations is increased, and the vibration can be further reduced as compared with the low speed rotation.

In the present embodiment, two cylinders are targeted, but even in a multi-cylinder type having three or more cylinders, when the number of cylinders is n, the phase of each cylinder is (360 / n) degrees. The same effect can be obtained by shifting each.

[0018]

According to the present invention, it is possible to provide a rotary compressor having high durability and low vibration as a rotary compressor.

[Brief description of drawings]

FIG. 1 is a side sectional view of a two-cylinder rotary compressor according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along line I-I in FIG.

FIG. 3 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. 4 is an explanatory diagram showing torque fluctuations of the two-cylinder rotary compressor shown as one embodiment of the present invention.

FIG. 5 is a sectional view of a pump portion of a conventional rotary compressor.

FIG. 6 is an explanatory diagram showing torque fluctuations in a single cylinder and two cylinders of a conventional rotary compressor.

[Explanation of symbols]

2 ... 2nd cylinder, 2a ... Cylindrical inner peripheral surface, 3 ... 1st plate member, 3a, 5a ... Boss part, 3b, 5b ... Hole part, 4
... second plate member, 5 ... third plate member, 6 ... bolt, 7 ... chamber, 8 ... motor stator part, 9 ... motor rotor part, 10 ... crank shaft, 10a, 10
b ... Shaft pin portion, 11, 12 ... Rollers, 13, 14
... vanes, 15, 16 ... space, 18 ... first side chamber, 19 ... second side chamber 21, 22, 22 ... discharge valve,
23, 24 ... Discharge valve retainer, 25 ... Discharge port.

Claims (1)

[Claims] 1. A plurality of cylinders having a cylindrical inner peripheral surface, a plurality of plate members closing both ends of the cylindrical inner peripheral surface of each of the plurality of cylinders, and the cylinder and the plate member. A plurality of rollers, each of which has a cylindrical outer peripheral surface that revolves while maintaining a minute gap between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface of the cylinder, in each of the plurality of enclosed spaces. A plurality of drive chamber parts for giving orbital motion to the cylinder, a plurality of spaces surrounded by the cylindrical inner peripheral surface of the cylinder, the cylindrical outer peripheral surface of the roller, and the plate member are further partitioned into the plurality of spaces. A multi-cylinder type rotary having a vane as a constituent element and compressing gas in each compression chamber by utilizing the fact that the respective volumes of the plurality of spaces change with the orbital motion of each of the plurality of rollers. In compressor, said vane and said roller, in a state where the central axis is parallel to each other of the cylindrical outer peripheral surface of the roller and parallel to two planes of the vanes,
The vane is connected or integrally molded, and the vane swings around one axis on the cylinder parallel to the central axis of the cylindrical inner peripheral surface of the cylinder and moves back and forth in a plane including the one axis. A rotary compressor having a structure that is supported by the cylinder so that