JP2002021751A - Rolling piston type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a lightweight and highly efficient rolling piston type compressor. SOLUTION: This rolling piston type compressor is formed as a structure that a roller 9 and a vane 10 are integrated, and advancing-retreating motion is generated in the vane by revolving motion of the roller, and in that case, lubricating oil is supplied to respective sliding parts by using the fact that a space housing a tip part of the vane repeats an increase-decrease in the volume.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling piston type positive displacement machine in which a roller and a vane are integrated, and more particularly to a rolling piston type compressor suitable for compressing gas.

[0002]

2. Description of the Related Art In a conventional rolling piston type compressor, a lubricating mechanism for a sliding portion is, for example, disclosed in Japanese Patent Laid-Open No. 4-308389, in which lubricating oil is maintained at a discharge pressure or the like. The oil was stored in a high-pressure chamber such as a motor chamber, and was supplied by differential pressure through an oil supply path to each sliding portion.

[0003]

First, in the prior art, since the lubricating oil is supplied to the sliding portion by a differential pressure, a differential pressure is generated between the sliding portion and the sliding portion in a high-pressure atmosphere. Since there is no lubrication oil, it is difficult to supply lubricating oil, and there is a problem that the reliability of the compressor is reduced. Also, the lubricating oil supplied to the sliding portion by the differential pressure eventually flows out to the low-pressure portion, and the working gas such as the refrigerant dissolved therein leaks from the high-pressure portion to the low-pressure portion. There is a problem that the performance of the device is reduced.

[0004] Next, in the above-mentioned conventional technique, it is general to use a large-volume space suitable for oil separation as an oil storage space.
In order to supply oil at a differential pressure, this must be a high-pressure chamber, and there is a problem that it is difficult to reduce the weight of the compressor because it is necessary to ensure a sufficient plate thickness of the container in order to guarantee the pressure resistance. This problem may become more serious if the new refrigerant that is to be used in the future to protect the ozone layer in the refrigeration and air conditioning equipment is a refrigerant having a higher pressure than the current refrigerant.

Further, in the prior art, when the motor chamber is used as an oil storage space in a hermetic compressor or the like, the motor chamber must be a high-temperature, high-density high-pressure chamber, and the coil temperature of the motor rises. Therefore, there is a problem in that the reliability and efficiency are reduced due to the above, and the efficiency is reduced due to the stirring loss of the motor rotor rotating in the high-density atmosphere.

An object of the present invention is to solve the above-mentioned problems caused by the conventional lubrication mechanism, and to provide a rolling piston compressor excellent in lightness, reliability and performance.

[0007]

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rolling piston type compressor in which a plate-like vane is radially projected from a cylindrical outer peripheral surface of a roller to be joined or integrally formed, and the revolving motion of the roller is achieved. With the structure in which the tip of the vane is repeatedly increased and decreased in volume, the vane storage space is used as an oil storage space when the vane exits from the storage space. This is achieved by providing a communicating hole and a hole communicating with the sliding portion when the vane enters the storage space.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS First, according to the structure for solving the above-mentioned problem, even if there is not enough differential pressure between the oil storage section and the sliding section, the vane advances and retreats in the middle of the oil supply path. Pressure for supplying lubricating oil can be generated.
Further, since the lubricating oil does not need to leak from the high-pressure part to the low-pressure part finally, the leakage of the working gas accompanying this is reduced and the efficiency is improved.

Next, since the vane is combined with or integrally formed with the roller, there is no need to apply a high back pressure to the tip of the vane in order to secure contact between the vane and the roller.
It is possible to reduce the pressure in the space containing the tip of the vane. When the space where the tip of the vane is stored becomes low pressure,
Even if the pressure of the oil storage space is low, there is no problem in refueling, the required pressure resistance of the container surrounding the oil storage space is reduced, and the weight of the compressor can be reduced.

Further, in a hermetic compressor or the like, a motor chamber generally used as an oil storage space can be a low-pressure chamber.
The temperature and the density in the motor chamber are low and the density is low, so that the reliability and efficiency are improved by lowering the coil temperature of the motor, and the efficiency is improved by reducing the stirring loss due to the lower density of the atmospheric gas in the motor rotor. Hereinafter, an embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a cross-sectional view showing a rolling piston type compressor according to a first reference example of the present invention, FIG. 2 is a cross-sectional view taken along line AA in FIG. 1, and FIG. FIG. 4 is a sectional view showing a rolling piston type compressor according to a second embodiment of the present invention, and FIG. 5 is a sectional view showing a rolling piston type compressor according to an embodiment of the present invention. FIG. 6 is a side sectional view showing the compressor, and FIG.
It is explanatory drawing of movement of each component in BB cross section of FIG.

In the first embodiment of the present invention shown in FIGS. 1 to 3, a cylinder 1 has a cylindrical inner peripheral surface 1a at the center.
Are formed, and the first plate member 2 and the second plate member 3 are fixed by bolts 4 so as to close both ends thereof. The first plate member 2 and the second plate member 3 have bearing portions 2a and 3a formed at the center, respectively, and rotatably support the crankshaft 5. At this time, the first plate member 2 and the second plate member 3 are fixed to the cylinder 1 such that the rotation axis of the crankshaft 5 coincides with the central axis of the cylindrical inner peripheral surface 1a of the cylinder. A rotor 6 of a compressor driving motor is provided on the crankshaft 5.
Has been fixed. An outer peripheral portion of the cylinder 1 is fixed to a chamber 7, and a stator 8 of a compressor driving motor is fixed to the chamber 7 so as to be coaxial with the rotor 6. The crankshaft 5 has a crankpin portion 5a formed in a portion inside the cylindrical hole portion 1a of the cylinder, and the cylindrical inner peripheral surface of the roller 9 rotates on the cylindrical outer peripheral surface of the crankpin portion 5a. Inserted as possible. The dimensions of each part are determined so that the gap between the cylindrical outer periphery of the roller 9 and the cylindrical inner peripheral surface 1a of the cylinder is small. Further, a vane 10 is integrally fixed to one portion of the cylindrical outer periphery of the roller 9 by welding or the like. At this time, two parallel planes of the vane 10 are aligned with the center axis of the roller 9. It is fixed so as to be parallel. A cylindrical hole 1b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a is formed below and outside the cylindrical inner peripheral surface 1a of the cylinder. The side communicates with the space in the center of the cylinder and another hole 1c provided outside the cylindrical hole 1b. The vane 10 is inserted into the cylindrical hole 1b and the hole 1c.
and a sliding member 11 having a flat surface slidably in contact with the flat surface of the vane 10 and a cylindrical surface slidably in contact with the cylindrical surface of the cylindrical hole 1b. As a result, the vane 10 is supported by the cylinder 1 such that the vane 10 can move forward and backward toward the central axis of the cylindrical hole portion 1b, and can swing around the central axis. The tip of the vane 10 on the side opposite to the joint with the roller 9 moves in the hole 1c and does not interfere with the cylinder 1.

With the above configuration, when the crankshaft 5 is rotated by the compressor driving motor, the roller 9 revolves with the crankpin portion 5a. FIG. 3 shows the roller 9 when the crankshaft 5 rotates by 90 °.
FIG. 5 is a view showing the movement of the vane 10 integrated with the roller, and a roller 9 is provided at the center of the crank pin portion 5a such that the integrated vane 10 always faces the center line of the cylindrical hole portion 1b of the cylinder. The center revolves while oscillating at a slight angle in the plane of FIG. 3 around the axis. The vane 10 moves forward and backward toward the central axis of the cylindrical hole 1b of the cylinder and swings around the central axis. The gap between the vane 10 and the cylindrical hole 1b of the cylinder is sealed by a sliding member 11. Is maintained by being inserted. 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, the second plate member 3, and the sliding member 11, and the rotation of the crankshaft 5 by the motor for driving the compressor. , The volume is repeatedly increased and decreased as shown in FIG.

A first side chamber 12 and a second side chamber 13 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 a suction port 14 attached to the first side chamber 12, passes through a gap around the outer periphery of the stator section 8 in the motor chamber space 15, and then increases the first plate when the compression chamber volume increases. A suction passage 2b formed in the member 2 and the cylinder 1;
1d, it is sucked into the compression chamber, is compressed when the volume of the compression chamber is reduced, and is discharged from a discharge port (not shown) formed in the second plate member 3 through a discharge valve 16 and a discharge valve holder 17. After that, it flows out of the compressor from a discharge port 18 provided in the second side chamber 13.

In this embodiment, in particular, the working gas is sucked into the compression chamber after passing through the motor chamber, and the motor chamber space 15 has a low pressure and is used as a lubricating oil storage space. I have. A space 19 formed by closing both axial ends of the hole 1c of the cylinder with the first plate member 2 and the second plate member 3 is formed by the communication passage 2c formed in the first plate member 2 in the motor chamber space 15. The oil reservoir is communicated with the bearings 2a and 3a by communication passages 2d and 3b formed in the first plate member and the second plate member, respectively. A lubrication path is configured. The communication passage 2c of the first plate member is provided with a check valve 20 that allows the flow of the lubricating oil from the oil storage section to the bearings 2a and 3a, but restricts the flow of the lubricating oil in the opposite direction. As a result, when the volume of the space 19 is increased by the reciprocating motion of the vane 10, the lubricating oil that has passed through the check valve 20 and flowed into the space 19 from the oil storage unit is discharged from the vane 10.
When the volume of the space 19 is reduced due to the forward and backward movement of the crankshaft 5, it is impossible to return to the oil storage section by the check valve 20, and is pushed out to the bearings 2 a, 3 a through the communication passages 2 d, 3 b. Provides lubrication when rotating. After that, a part thereof flows into the inside of the roller 9, and lubrication between the cylindrical inner peripheral surface of the roller 9 and the cylindrical outer peripheral surface of the crank pin portion 5a, and the axial end surface of the roller 9 and the first plate member. The lubrication between the second plate member 2 and the second plate member 3 is performed, and another part passes through a communication passage 5b formed in the center of the crankshaft 5 from the back of the bearing portion 3a of the second plate member. Reflux to 15. Vane 10 and sliding member 1
Part of the lubricating oil that has once flowed into the space 19 due to the reciprocating motion of the vane 10 is used for lubrication between the sliding member 1 and the sliding member 11 and the cylindrical hole 1b of the cylinder. For convenience in processing when forming the communication passages 2d, 3b, etc.,
In this embodiment, sealing plugs 21 and 22 are used, and the communication passages 2c and 2d are shown in FIG. 1 as if they are formed in the same cross section for convenience. As can be seen from FIG. 1, actually, they are formed at positions shifted from each other in the direction perpendicular to the paper surface of FIG.

As described above, according to this embodiment, first,
No lubrication by differential pressure is adopted, and reliable lubrication can be performed even if there is not enough differential pressure between the oil storage section and each sliding section, improving the reliability of the compressor and improving lubrication. Since there is no need to finally leak the oil from the high-pressure section to the low-pressure section, there is an effect that the leakage of the working gas associated therewith is reduced and the efficiency of the compressor is improved.

Next, according to this embodiment, since the vane and the roller are integrated, there is no need to apply a high back pressure to the tip of the vane to maintain the contact between them.
It is possible to reduce the pressure in the space containing the tip of the vane. When the space where the tip of the vane is stored becomes low pressure,
Since there is no problem in refueling, it is possible to reduce the pressure in the motor room space in which the oil storage section is located, reduce the required pressure resistance of the container surrounding the space, and reduce the weight of the compressor.

Further, since the motor chamber can be made into a low-pressure chamber, the gas in the motor chamber has a low temperature and a low density, the efficiency of the compressor is improved due to a decrease in the temperature of the coil of the motor, and the low density of the atmospheric gas in the motor rotor is reduced. The compressor efficiency is improved by the reduction of the stirring loss accompanying the conversion.

FIG. 4 shows a second embodiment of the present invention. The second reference example has almost the same configuration as the first reference example. However, the check valve 20 is incorporated in the communication passage 2c of the first plate member of the first reference example. An orifice 23 is incorporated in the communication passage 2c of the first plate member 2 of the reference example. The flow path shape of the orifice 23 is tapered so that the cross-sectional area decreases in the direction from the oil storage section to the space 19, and the flow of the lubricating oil in the direction from the oil storage section to each sliding section in the entire oil supply path. The passage resistance of the flow of the lubricating oil in the direction from each sliding portion to the oil storage portion is set to be larger than the passage resistance. As a result, vane 10
When the volume of the space 19 is smaller than the amount of the lubricating oil flowing into the space 19 from the oil reservoir through the orifice 23 when the volume of the space 19 is increased by the reciprocating motion of the space 19, The amount of the lubricating oil returning to the oil storage portion is small, and the difference is supplied to the bearing portions 2a, 3a through the communication passages 2d, 3b.

Therefore, the same effect can be obtained because the same oil supply mechanism as that of the first embodiment can be formed. However, in the second embodiment, a simple and movable valve can be used instead of the check valve. By adopting an orifice without a section, the compressor becomes cheaper.

FIGS. 5 and 6 show an embodiment of the present invention.
In this embodiment, as in the second embodiment, only the oil supply path of the first embodiment is changed, but in connection with this, the hole 24c of the cylinder 24 is widened and the length of the vane 2 is increased.
5 can be stored. The other end of the communication passage 26c formed in the first plate member 26 and having one end open to the oil storage portion has both ends of the cylinder hole 24c closed by the first plate member 26 and the second plate member 27. The opening 28 is shown in FIG.
As shown in FIG. 6D, while the vane 25 enters the space 28 and the volume of the space 28 is reduced, the vane 25 is closed by the axial end surface of the vane 25, and as shown in FIG. 2
5 exits the space 28 and is fully open while the volume of the space 28 is increasing. On the other hand, a communication passage 26 formed in the first plate member 26 and having one end opened to the bearing portion 26a.
The other end of the space d also communicates with the space 28, and the opening of the vane 25 extends out of the space 28 while the volume of the space 28 is increasing, as shown in FIG. The vane 25 enters the space 28 and is fully opened while the volume of the space 28 is reduced. The other end of the communication passage 27b formed in the second plate member 27 and having one end opened to the bearing portion 27a is also a space 28.
However, the opening is formed at a position facing the opening of the communication passage 26d (not shown), and is configured to be opened and closed in the same manner as the opening of the communication passage 26d. As a result, while the vane 25 goes out and the volume of the space 28 is increasing, only the state of communication between the space 28 and the oil storage portion is good, and lubricating oil is sucked into the space 28. In addition, while the volume of the space 28 is decreasing after the vane 25 enters, only the communication between the space 28 and the bearings 26a and 27a is good, and the lubricating oil is supplied to the bearings 26a and 27a. In FIG. 5, the communication passages 26c and 26d are shown as if they are formed in the same cross section for convenience. However, as can be seen from FIG. Are formed at positions shifted from each other.

Therefore, the same effect as that of the reference example can be obtained because the oil supply mechanism can be configured similarly to each reference example. However, in the embodiment of the present invention, in particular, the check valve, the orifice, etc. The above effects can be obtained without incorporating components, and a more inexpensive compressor can be provided.

[0022]

According to the present invention, in a rolling piston type compressor in which a vane and a roller are integrated, a reliable oil supply and a low pressure in a motor room space are possible, and a light weight and high efficiency rolling piston type compressor is provided. Can be provided.

[Brief description of the drawings]

FIG. 1 is a side sectional view showing a rolling piston type compressor for explaining a first reference example of the present invention.

FIG. 2 is a sectional view taken along line AA in FIG.

FIG. 3 is an explanatory diagram of the movement of each component in FIG. 2 when a motor for driving the compressor is rotated by 90 °.

FIG. 4 is a sectional view showing a rolling piston type compressor according to a second reference example of the present invention.

FIG. 5 is a sectional view showing a rolling piston type compressor according to the embodiment of the present invention.

FIG. 6 is an explanatory view of the movement of each part in the BB section of FIG. 5 when the motor for driving the compressor is rotated by 90 ° at a time.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Cylinder, 2 ... First plate member, 2a ... Bearing part,
2c: communication passage, 3: second plate member, 3a: bearing portion, 3b: communication passage, 4: bolt, 5: crankshaft, 5a: crankpin portion, 5b: oil passage, 6: motor rotor portion, 7 ... chamber, 8 ... motor stator part,
9 ... roller, 10 ... vane, 12 ... first side chamber, 13 ... second side chamber, 14 ... inlet, 15 ...
Motor room space, 16: discharge valve, 17: discharge valve holder, 1
8 ... Discharge port, 20 ... Check valve.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Takeshi Kono 502 Kandachi-cho, Tsuchiura-shi, Ibaraki F-term in Machine Research Laboratory, Hitachi, Ltd. (Reference) 3H029 AA04 AA11 BB01 CC03 CC05 CC24 CC25 CC32

Claims (1)

[Claims] 1. A cylinder having a cylindrical inner peripheral surface, a plurality of side plates closing both ends of the cylindrical inner peripheral surface of the cylinder, and a space surrounded by the cylinder and the plurality of side plates. Among them, a roller whose orbital motion revolves while its cylindrical outer peripheral surface always keeps a minute gap with the cylindrical inner peripheral surface of the cylinder, a drive mechanism for giving orbital motion to the roller, and the cylindrical shape of the roller A plate-like vane which is radially projected from the outer peripheral surface and is joined or integrally formed, and a swing motion about one axis on a cylinder parallel to a central axis of the cylindrical inner peripheral surface of the cylinder and the one axis. And a support structure for supporting the vane so that the vane can move forward and backward in a plane including the roller. In the rolling piston type compressor, the tip of the vane protruding from the cylindrical outer peripheral surface of the roller is collected. Utilizing the fact that the space that has been repeatedly increased and decreased in volume as the vane moves forward and backward, the vane storage space has a hole that communicates with the oil storage space when the vane exits the storage space, and the vane has a storage space. A rolling piston type compressor comprising a hole communicating with a sliding portion when entering a space.