JP2002371973A - Rocking piston type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rocking piston type compressor preventing impairment of compressed gas sealing performance, reducing wearing between a sliding member and a sliding hole by certainly supplying lubricating oil into a load supporting position of the sliding hole, and having high performance and high durability. SOLUTION: A platy vane 8b is projected our from a roller 8a, thereby dividing the inside of a cylinder 1 into a sucking chamber 12 connecting to a sucking port 3a and a compressing chamber 11 connecting to a discharging port 3b. A sliding hole 1b into which the vane 8a is inserted is formed on the outside of an cylindrical inner peripheral surface 1a of the cylinder 1, and a sliding member 10 is put in a space with the sliding hole 1b on both sides of the vane 8a. The circumferential length of an abutting surface between the sliding member 10 and the sliding hole 1b in the sucking port 3a side is made to be shorter than the circumferential length of an abutting surface between the sliding member 10 and the sliding hole 1b in the discharging port 3b side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oscillating piston compressor, and more particularly, to an oscillating piston compressor used in a refrigeration / air-conditioning system.

[0002]

2. Description of the Related Art Conventionally, as a rotary compressor in which a roller and a vane are widely used separately in a refrigeration / air-conditioning system and the like, an electric element having a stator and a rotor in a closed container, The driven compression element is housed, and the compression element is configured such that a roller rotatably fitted to the eccentric portion of the drive shaft eccentrically rotates in the cylinder by the rotation of the drive shaft, and the cylinder is moved by the vane pressed by the roller. The interior is partitioned into a suction chamber and a compression chamber, and the suction gas sucked from the suction pipe is compressed by the compression element, and the compressed refrigerant gas is discharged into the closed container,
Some are discharged from a discharge pipe to an external refrigeration cycle (prior art 1). However, the prior art 1 has the strictest lubrication condition for the contact portion between the vane and the roller, which has a high surface pressure due to line contact, and there is a reliability problem that the sliding portion between the vane and the roller is particularly worn. Was.

In order to solve the problem of the prior art 1, there is a rotary compressor in which a roller and a blade are integrated, as disclosed in Japanese Patent Application Laid-Open No. 6-336989 (prior art 2). This rotary compressor has a discharge pressure in a closed casing, a cylinder having a cylinder chamber, a roller fitted to an eccentric shaft portion of a drive shaft and provided inside the cylinder chamber, and protruding from an outer peripheral portion of the roller. A blade that partitions the interior of the cylinder chamber into a low-pressure chamber that communicates with the suction port and a high-pressure chamber that communicates with the discharge port, and has a receiving groove for receiving the protruding tip side of the blade so that it can advance and retreat freely. A swing bush held swingably in the hole, wherein at least one of the outer circumferential surface and the inner circumferential surface is swung between the outer circumferential surface of the swing bush and the inner circumferential surface of the holding hole. By providing symmetrically the oil reservoir formed by recessing in the direction perpendicular to the moving direction, it is possible to reduce insufficient lubrication of the contact surface between the swinging bush and the holding hole,
Some of them can improve lubricity and reduce sliding loss between them.

[0004]

However, the prior art 2 does not disclose the direction of load applied to the oscillating bush due to the gas compression action or the load supporting position of the holding hole. For this reason, the seal width is reduced by the oil reservoir recess formed on the outer circular arc surface of the swinging bush on the discharge port side, so that there is a problem that high-pressure gas in the compression chamber leaks to the outside of the cylinder and performance is likely to deteriorate. Was. In addition, since the suction port is located at a position away from the blade, the crank angle for closing the suction port increases, and the actual suction volume decreases,
There has been a problem that the angle between the discharge port and the suction port is increased, the gas is more susceptible to gas re-expansion in the clearance volume of the discharge port, and the volumetric efficiency of the compressor is reduced. Furthermore, since the inside of the closed container is in an atmosphere of the discharge pressure, supply of lubricating oil by differential pressure can be expected. However, the refrigerant gas in the closed container easily dissolves in the lubricating oil, the amount of refrigerant increases, and the sealed container has high pressure resistance. The document does not disclose that the container needs to be a container and the lubrication improvement of the sliding portion between the swing bush and the holding hole when the pressure in the closed container is lower than the discharge pressure is not described.

SUMMARY OF THE INVENTION It is an object of the present invention to reliably supply lubricating oil to a load supporting position of a sliding hole without impairing the compressed gas sealing property, to reduce wear between the sliding member and the sliding hole, It is an object of the present invention to provide a swinging piston type compressor having high performance and high reliability.

Another object of the present invention is to reduce the amount of refrigerant used and to reduce the thickness and weight of the sealed container by lowering the pressure in the sealed container to a pressure lower than the discharge pressure, and to achieve high performance without impairing the compressed gas sealability. To provide a reliable swinging piston type compressor that can secure lubrication, and can reliably supply lubricating oil to the load supporting position of the sliding hole, and reduce wear of the sliding member and the sliding hole. It is in.

Another object of the present invention is to reduce the crank angle for closing the suction port to increase the actual suction volume, and to reduce the effect of gas re-expansion in the clearance volume of the discharge port to reduce the volumetric efficiency of the compressor. Can be improved,
Furthermore, the lubrication of the sliding member and the sliding hole can be reduced by promoting the supply of lubricating oil to the load supporting position of the sliding hole without impairing the gas sealing performance of the sliding member on the discharge port side, and high performance. And a highly reliable swing piston type compressor.

[0008]

A first feature of the present invention to achieve the above object is to provide a cylinder having a cylindrical inner peripheral surface and an end for closing both ends of the cylindrical inner peripheral surface of the cylinder. A plate, a roller whose orbital motion revolves while maintaining a small gap between the cylindrical outer circumferential surface and the cylindrical inner circumferential surface of the cylinder in a space surrounded by the cylinder and the end plate; A drive mechanism for providing motion, a plate-shaped vane projecting radially from the cylindrical outer peripheral surface of the roller to partition the interior of the cylinder into a suction chamber communicating with a suction port and a compression chamber communicating with a discharge port, and a cylinder of the cylinder. A sliding hole formed outside the inner peripheral surface with a central axis parallel to the central axis and into which the vane is inserted, and incorporated into two spaces formed between the sliding holes on both sides of the vane. Sliding contact with sliding hole And two sliding member having a flat portion slidably contacting with the cylindrical surface portion to the flat portion of the vane,
Oscillating piston type compressor equipped with
The circumferential length of the contact surface between the sliding member on the suction port side and the sliding hole is shorter than the circumferential length of the contact surface between the sliding member on the discharge port side and the sliding hole.

A second feature of the present invention is that a cylinder having a cylindrical inner peripheral surface, an end plate for closing both ends of the cylindrical inner peripheral surface of the cylinder, and the cylinder surrounded by the cylinder and the end plate. A roller that revolves while maintaining a small gap between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface of the cylinder in the space,
A drive mechanism for revolving the roller, and a plate-shaped vane projecting radially from the cylindrical outer peripheral surface of the roller to partition the inside of the cylinder into a suction chamber communicating with a suction port and a compression chamber communicating with a discharge port, Two spaces formed between a sliding hole formed outside the cylindrical inner peripheral surface of the cylinder and having a central axis parallel to the central axis and into which the vane is inserted, and the sliding holes on both sides of the vane. A swinging piston type compressor having, in a sealed container, two sliding members having a cylindrical surface portion slidably in contact with the sliding hole and a flat portion slidably in contact with the flat portion of the vane. In the above, the pressure in the closed container is lower than the discharge pressure, and a notch is formed by cutting out a corner formed by the sliding hole on the suction port side and the cylindrical inner peripheral surface of the cylinder. Communicate with Lies in the formation of the port suction to so that.

A third feature of the present invention is that a cylinder having a cylindrical inner peripheral surface, an end plate for closing both end portions of the cylindrical inner peripheral surface of the cylinder, and a cylinder surrounded by the cylinder and the end plate. A roller that revolves while maintaining a small gap between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface of the cylinder in the space,
A drive mechanism for revolving the roller, and a plate-shaped vane projecting radially from the cylindrical outer peripheral surface of the roller to partition the inside of the cylinder into a suction chamber communicating with a suction port and a compression chamber communicating with a discharge port, Two spaces formed between a sliding hole formed outside the cylindrical inner peripheral surface of the cylinder and having a central axis parallel to the central axis and into which the vane is inserted, and the sliding holes on both sides of the vane. A swinging piston type compressor having, in a sealed container, two sliding members having a cylindrical surface portion slidably in contact with the sliding hole and a flat portion slidably in contact with the flat portion of the vane. In this case, the inside of the closed container is set at the discharge pressure, and the slide port on the suction port side is partially cut off at the vane tip side.

[0011]

Embodiments of the present invention will be described below with reference to the drawings. In the second and subsequent embodiments, some of the components common to the first embodiment are omitted, and
A duplicate description will be omitted. The same reference numerals in the drawings of the respective embodiments indicate the same or corresponding components.

A first embodiment of the present invention will be described with reference to FIGS.

First, the overall configuration and operation of a horizontal swing piston type compressor according to a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a main part of a horizontal oscillating piston type compressor according to a first embodiment of the present invention, and FIG.
FIG. 3 is a sectional view illustrating the operation of the compression element of FIG. 1.

In the oscillating piston type compressor of this embodiment, an electric element, a compression element, and a drive shaft 4 for connecting both the electric element and the compression element are arranged in a closed vessel 6, and the inside of the closed vessel 6 is suctioned at a pressure lower than a discharge pressure. Pressure. The electric element has a stator 7 and a rotor 5. The compression element has a compression mechanism and an oil supply mechanism. The compression mechanism includes a cylinder 1 and
The cylinder 1 comprises a swinging piston 8 rotatably arranged in the cylinder 1, a main bearing 2 and an auxiliary bearing 3 which also serve as end plates for closing the openings at both ends of the cylinder 1. The refueling mechanism is
Pump hole 1c of cylinder 1, vane 8b, suction fluid diode 18, discharge fluid diode 19, oil supply pipe 2
9, a spiral groove 31 forming an oil supply passage formed in the drive shaft 4, an oil pocket 32 intermittently communicating with the roller 8a and the suction chamber 12, and the like.

The cylinder 1 has a cylindrical inner peripheral surface 1a at the center.
The main bearing 2 and the sub-bearing 3
And are closed. The main bearing 2 and the sub bearing 3 also rotatably support the drive shaft 4. A rotor 5 of an electric element is fixed to the drive shaft 4. The outer periphery of the cylinder 1 is a sealed container 6
And the airtight container 6 has a stator 7 of an electric element.
Are fixed so as to be coaxial with the rotor 5. And
The drive shaft 4 is formed with an eccentric portion 4 a at a portion located within the cylindrical inner peripheral surface 1 a of the cylinder 1.

The cylindrical inner peripheral surface of the roller 8a of the swing piston 8 is rotatably fitted to the eccentric portion 4a. The dimensions of each part are determined so that the gap between the seal portions where the cylindrical outer peripheral surface of the roller 8a and the cylindrical inner peripheral surface 1a of the cylinder 1 are close to each other is very small. A plate-like vane 8b is integrally formed on the cylindrical outer peripheral surface of the roller 8a so as to protrude. A sliding hole 1b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a is formed outside the cylindrical inner peripheral surface 1a of the cylinder 1; Is the cylindrical inner peripheral surface 1a of the cylinder 1
And a pump hole 1c which allows the tip end of the vane provided outside the sliding hole 1b to move forward and backward. The pump hole 1c has a central axis parallel to the central axis of the sliding hole 1b.

The vane 8b extends so as to be inserted into the sliding hole 1b and the pump hole 1c. Between the vane 8b and the sliding hole 1b, a sliding member 10 slidably in contact with the side surface of the vane 8b and slidably in contact with the cylindrical surface of the sliding hole 1b sandwiches the vane 8b from both sides. It is built to fit. As a result, the vane 8b moves in the sliding hole 1b.
And a swinging motion about the central axis are supported. The tip of the vane 8b moves forward and backward in the pump hole 1c and does not interfere with the cylinder 1.

With the above configuration, when the drive shaft 4 is rotated by the electric element, the oscillating piston 8
A revolving motion accompanied with swinging is performed in the cylinder 1 together with a.
FIG. 3 is a diagram showing the movement of the swing piston 8 when the drive shaft 4 rotates by 60 degrees. As is apparent from FIG. 3, the center of the roller portion 8a while performing a swinging motion at a slight angle around the center axis of the eccentric portion 4a so that the vane portion 8b always faces the center axis direction of the cylindrical hole portion 1b. Make an orbital motion. The vane portion 8b performs a reciprocating motion toward the central axis of the cylindrical hole portion 1b and a swinging motion around the central axis. The sealing of the gap between the vane portion 8b and the cylindrical hole portion 1b is maintained by inserting the sliding member 10. Accordingly, the compression chamber 11 (the hatched portion in FIG. 3), which is a closed space, is formed by the cylinder 1, the oscillating piston 8, the main bearing 2, the auxiliary bearing 3, and the sliding member 9.
A suction chamber 12, which is a suction space, is formed, and as the drive shaft 4 is rotated by the electric element, a compression action of the refrigerant gas which repeatedly increases and decreases in volume is performed as shown in FIG.

With this configuration, the refrigerant gas is sucked into the closed vessel 6 from the suction pipe 13 attached to the closed vessel 6, passes through the suction passage 14, and then passes through the suction port 3a formed in the sub bearing 3. To be sucked into the suction chamber 12. Refrigerant gas sucked into the suction chamber 12 is transferred to the compression chamber 11 immediately after the rotation of the drive shaft 4 advances and the roller 8a passes through the notch 1d communicating with the suction port 3a. Is reduced.
The compressed refrigerant gas pushes up a discharge valve (not shown) from a discharge port 3b formed in the sub bearing 3 and enters a discharge chamber 3c formed by the sub bearing 3 and the discharge cover 15,
Thereafter, the refrigerant is discharged from the discharge pipe 16 to a refrigeration cycle outside the compressor.

As described above, in the present embodiment, the suction pipe 13
Is temporarily sucked into the closed vessel 6, and the pressure in the closed vessel 6 becomes the suction pressure. By setting the inside of the closed container 6 to the suction pressure, there are the following advantages. (1) Since the electric element is not heated by the compressed high-temperature refrigerant gas and is cooled by the low-temperature refrigerant gas, the temperatures of the rotor 5 and the stator 7 decrease, the motor efficiency is improved, and the Performance can be improved. (2) Since the pressure of the lubricating oil 17 supplied to the inner surface of the roller 8a also becomes the suction pressure, there is no excessive oil supply due to the differential pressure into the suction chamber 12 as in the high-pressure system. By optimizing the supply, the efficiency of the compressor can be improved. (3) Refrigerant compatible with oil such as chlorofluorocarbon has a low pressure, so that the proportion of the refrigerant dissolved in the oil is reduced, so that the foaming phenomenon in the bearing is less likely to occur and the reliability is improved. Can be. Further, in the case of a flammable refrigerant such as propane or isobutane, the amount of the refrigerant used is reduced, and safety can be improved. (4) The pressure resistance of the sealed container 6 can be reduced, and the thickness and weight of the sealed container 6 can be reduced.

Further, in the swinging piston type compressor shown in the present embodiment, since the roller 8a and the vane 8b are integrated, the vane is applied to the roller like a rotary compressor in which the roller and the vane are separated. There is no need to apply a high back pressure to the vane for pressing, and it is easy to apply to a structure in which the inside of the closed container is set to the suction pressure.

The lubricating oil 17 stored at the bottom of the closed container 6
Works as follows. In FIG. 1, the rotation of the drive shaft 4 causes the vane 8b to move into the pump hole 1c.
, The volume in the pump hole 1c changes. The lubricating oil 17 stored in the bottom of the sealed container 6 is sucked from the suction fluid diode 18 by the pump action due to the volume change, passes through the discharge fluid diode 19, passes through the oil supply pipe 20, and forms a spiral groove formed in the drive shaft 4. It is supplied to each bearing sliding portion through 31 to perform a lubricating action, and returns to the inside of the closed container 6 again.

A part of the lubricating oil 17 that has lubricated the eccentric portion 4a flows out to the inner surface of the roller portion 8a, and is provided in an oil pocket 32 provided on the end surface of the main bearing 2 which alternately moves between the suction chamber 12 and the inner surface of the roller portion 8a. As a result, the air is supplied to the suction chamber 12 as shown by the solid arrow in FIG. In the refueling by the oil pocket 32, an appropriate amount of lubricating oil can be supplied to the suction chamber by the operation of the positive displacement pump without depending on the differential pressure, so that intake heating loss due to excessive refueling can be reduced. From the experiments conducted by the present inventors, it was found that the amount of oil supplied for internal lubrication suitable for the performance of the oscillating piston compressor is in the range of about 0.1% to 1.0% by mass in terms of the oil circulation rate of the refrigeration cycle. It is clear. Here, the same effect can be obtained even if the oil pocket 32 is provided on the end face side of the sub bearing 3 and the spiral groove 31 is provided on the main bearing 2 and the sub bearing 3 side.

Further, as shown in FIG.
The refrigerant gas foamed from the lubricating oil 17 passing through 1 passes through the vent hole 4b, and the high-pressure refrigerant gas leaked from the compression chamber 10 into the inner surface of the roller portion 8a passes through the communication hole 4e, and The gas is discharged into the closed container 6 by the gas discharge hole 4c formed in the container.

Next, the sliding hole 1b and the sliding member of the cylinder 1 will be described with reference to FIGS. FIG. 4 is a polar diagram of a load vector acting on a sliding hole of a cylinder in the above-described oscillating piston type compressor, FIG. 5 is an explanatory diagram of a load acting position on an inner periphery of the sliding hole in the compressor, and FIG. It is a principal part perspective view which shows the structure around the sliding member in a machine.

FIG. 4 is a polar diagram (analysis result) showing a load vector representing the magnitude F of the load acting on the sliding hole 1b of the cylinder 1 and its direction φ. In FIG. 4, the center of the sliding hole 1b is taken as the origin of the coordinates, the lower side of the figure is the cylindrical inner peripheral surface 1a side of the cylinder 1, the right side of the figure is the suction port 3a side (shown as S side), The left side of the figure is the discharge port 3b side (shown as D side). The numbers shown in the characteristic curves in the figure represent the crank angle θ of the drive shaft 4. The calculation conditions are as follows: suction pressure Ps = 0.095M which is close to normal operating conditions in the summer of a refrigerator for a refrigerator using refrigerant R134a.
Pa, discharge pressure Pd = 1.04 MPa, rotation speed n = 6
0 rps.

As is clear from FIG. 4, the load acting on the sliding hole 1b on the suction port 3a side is
It can be seen that the load acting on the sliding hole 1b on the side is as large as twice or more, and that the direction also acts in a substantially constant direction. In addition, any of the sliding holes 1 on the suction port 3a side and the discharge port 3b side
It can also be seen that the load acting on b is small in the first half of the compression process corresponding to the crank angle θ = 0 to 180 °, and that most of the load is acting in the second half of the compression process when θ ≧ 180 °.
Furthermore, as is clear from FIGS. 4 and 5, the load on the suction port 3a acts on a narrow range of the inner circumference angle φ = 81 ° to 89 ° of the sliding hole 1b, and the load on the discharge port 3b slides. It acts on a narrow range of the angle φ = 320 ° to 333 ° of the inner circumference of the hole 1b.

Therefore, the sliding hole 1 with which the sliding member 10 is engaged
The inner peripheral shape of the cylinder 1 is set so that the inner peripheral length of the sliding hole 1b on the side of the suction port 3a with which the sliding member 10 engages is changed so that the inner peripheral length of the sliding port 1a is different between the suction port 3a side and the discharge port 3b side. A part 1d on the inner peripheral surface 1a side of the cylinder is cut out to make it shorter than the inner peripheral length of the sliding hole 1b on the discharge port 3b side. Thereby, the lubricating oil 17 supplied into the cylinder 1 is adhered to the surface of the sliding member 10 which is widely exposed, so that the lubricating oil can be reliably supplied to each load supporting position of the sliding hole 1b by the swinging motion. Therefore, abrasion of the sliding portion between the sliding member 10 and the sliding hole 1b can be reliably prevented, and the reliability of the compressor is secured. In this case, by forming the cutout portion 1d leaving a range of an angle φ = 81 ° to 89 ° at which a load is applied to the inner periphery of the sliding hole 1b, the sliding member 10 can be formed without impairing the reliability in terms of strength. The applied load can be sufficiently received by the remaining portion.

The inside of the closed vessel 6 is set to a suction pressure, and a notch 1d is provided on the inner wall side of the cylinder 1 which is in contact with the sliding hole 1b on the suction port 3a side, and the suction port 3a communicates along the notch 1d. Is formed, the crank angle θ for closing the suction port 3a can be reduced, so that the actual suction volume can be increased, and the angle α between the discharge port 3b and the suction port 3a can be reduced. , The influence of the gas re-expansion in the clearance volume is reduced, and the volumetric efficiency of the compressor can be remarkably improved.

The refrigerant gas that has entered the cylinder 1 through the suction port 3a shown by a two-dot chain line in FIG.
0, the lubricating oil mixed in the gas is separated and adheres to the outer surface of the sliding member 10, and the lubricating oil supplied from the oil pocket 32 to the suction chamber 32 is
The lubricating oil adhered to the outer surface of the sliding member 10
Is easily supplied to the load supporting position of the sliding hole 1b (the portion of the inner circumference of the sliding hole 1b where the angle φ = 81 ° to 89 °).

On the other hand, the load acting position of the sliding hole 1b on the discharge port 3b side (the angle φ of the inner circumference of the sliding hole 1b = 320)
(In the range of か ら ° to 333 °) is located in the vicinity of the pump hole 1c, so that the lubricating oil 17 easily filled in the pump hole 1c by the oscillating movement of the sliding member 10 and the pumping action of the vane 8b can be used. Will be supplied to the load supporting position.

As described above, according to this embodiment, the lubricating oil 17 can be reliably supplied to the load supporting position of the sliding hole 1b without impairing the sealing performance of the compressed gas (particularly on the discharge port side). Even in a low-pressure system in which the pressure in the sealed container 6 becomes the suction pressure, a swinging piston type compressor with high performance and high reliability can be provided.

Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 7 is a plan view of a main part of a cylinder in a swinging piston type compressor according to a second embodiment of the present invention. This embodiment is different from the first embodiment as described below.
The other points are basically the same as the first embodiment.

In this embodiment, the sliding hole 1 on the suction port 3a side
The notch 1e is also provided in the inner peripheral shape on the side of the pump hole 1c. With such a configuration, the lubricating oil 17 in the pump hole 1c is also easily supplied to the load supporting position of the sliding hole 1b on the suction port 3a side, and further promotes lubrication of the sliding hole 1b to improve reliability. can do. In this case, the circumferential length of the sliding hole 1b on the suction port side located between the two notches 1d and 1e and receiving the load of the sliding member 10 is determined by the angle φ at which the load is applied to the inner periphery of the sliding hole 1b. By setting the angle larger than the range of 50 ° to 120 ° in consideration of the strength of the cylinder 1 in the range of 81 ° to 89 °, it is possible to secure the strength reliability.

Next, a third embodiment of the present invention will be described with reference to FIGS.
Explanation will be made using 0. FIG. 8 is a longitudinal sectional view of a main part of a swinging piston type compressor according to a third embodiment of the present invention, and FIG.
FIG. 10 is a pole view of a load vector acting on a sliding hole of a cylinder in the swinging piston type compressor, and FIG.
FIG. 4 is an explanatory view of a load acting position on an inner periphery of a sliding hole in the compressor. This embodiment is different from the first embodiment as described below, and the other points are basically the same as the first embodiment.

The refrigerant gas is sucked into the suction chamber 12 of the cylinder 1 directly from the suction pipe 13 attached to the closed vessel 6 through the suction port 3a formed in the sub bearing 3.
The rotation of the drive shaft 4 advances, and the refrigerant gas sucked into the suction chamber 12 is transferred to the compression chamber 11 immediately after the roller 8a passes through the suction port 3a, and is compressed by reducing the volume of the compression chamber 11. You. The compressed refrigerant gas is supplied to the auxiliary bearing 3
A discharge valve (not shown) is pushed up from the discharge port 3b formed in the sub-bearing 3 and the discharge chamber 3c formed by the discharge cover 15, and the sub-bearing 3, the cylinder 1,
The gas is discharged into the closed vessel 6 through a gas passage 18 formed through the main bearing 2, and then discharged from a discharge pipe 16 attached to the closed vessel 6 to a refrigeration cycle outside the compressor.

The basic operation of the oscillating piston compressor of this embodiment is the same as that of the low-pressure horizontal oscillating piston compressor of the first embodiment, except that the pressure in the closed vessel 6 is high. (Discharge pressure), the lubricating oil 17 is also at a high pressure, and the load supporting position of the sliding hole 1b is different from that of the first embodiment.

FIG. 10 is a polar diagram of a load vector representing the magnitude F of the load acting on the sliding hole 1b of the cylinder 1 and its direction φ according to the present embodiment, and is analyzed under the same conditions as in the first embodiment. The result. As is apparent from FIG. 10, it is understood that the direction of load application in the high-pressure system is significantly different from that in the low-pressure system of the first embodiment. That is, the load on the suction port 3a acts on the range of the angle φ of the inner circumference of the sliding hole 1b from 110 ° to 145 °, and the load on the side of the discharge port 3b changes the angle φ of the inner circumference of the sliding hole 1b from 205 ° to 215 °. Act on the range.
The load acting on the sliding hole 1b on the suction port 3a side does not become zero during one rotation of the drive shaft 4, and it is understood that the load is always applied. This is because the lubricating oil 17 in the pump hole 1c has a high pressure.

Therefore, the sliding hole 1 with which the sliding member 10 engages
In order to make the inner peripheral shape of the sliding hole 1b different between the suction port 3a side and the discharge port 3b side, the sliding member 1
The inner peripheral length of the sliding hole 1b on the side of the suction port 3a with which 0 engages is shorter than the inner peripheral length of the sliding hole 1b on the side of the discharge port 3b by cutting out a part of the cylinder 1 on the side of the pump hole 1c. As a result, the high-pressure lubricating oil 17 in the pump hole 1c is supplied to the suction chamber 12
It is easy to supply to the load supporting position of the sliding hole 1b (the part of the inner circumference of the sliding hole 1b in the range of φ = 110 ° to 145 °) by the pressure difference between the sliding member 10 and the sliding hole. 1b can be prevented from being worn, and the reliability of the compressor can be ensured. In this case, by forming the cutout portion 1d leaving an angle φ of 110 ° to 145 ° at which a load is applied to the inner periphery of the sliding hole 1b, the sliding member 10 can be used without impairing the reliability in terms of strength. The applied load can be sufficiently received by the remaining portion.

Since the load acting position of the sliding hole 1b on the discharge port 3b side is located near the cylindrical inner peripheral surface 1a of the cylinder 1, the sliding member 10 easily flows into the cylinder 1 by the differential pressure due to the swinging motion. The lubricating oil 17 thus supplied is supplied to the load supporting position of the sliding hole 1b, and the friction loss can be reduced.

As described above, according to the present embodiment, the lubricating oil 17 can be reliably supplied to the load supporting position of the sliding hole without impairing the sealing performance of the compressed gas. And a high-performance and highly reliable swinging piston type compressor in a high-pressure system.

Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 12 is a configuration diagram of a refrigeration cycle of a refrigeration system according to a fourth embodiment of the present invention. This refrigeration cycle is a refrigeration cycle dedicated to refrigeration (cooling). In FIG. 12, reference numeral 21 denotes the oscillating piston type compressor of the first embodiment, 22 denotes a condenser, 23 denotes an expansion valve, and 24 denotes an evaporator.

By starting the oscillating piston compressor 21 of the present invention, the compressed high-temperature and high-pressure working gas is
As shown by the solid line arrow, it flows into the condenser 22 from the discharge pipe 16, where it radiates and liquefies, and is throttled by the expansion valve 23.
After being adiabatically expanded to a low temperature and a low pressure, the heat is absorbed and gasified by the evaporator 24, and then sucked into the swinging piston type compressor 21 again through the suction pipe 13. Here, since the refrigeration system shown in FIG. 12 is equipped with the oscillating piston compressor 21 of the present invention, a refrigeration system excellent in energy efficiency can be obtained. In particular, since the swinging piston type compressor 21 of the present invention has a low pressure in the closed vessel 6, the amount of high-temperature and high-pressure refrigerant flowing backward from the compressor into the evaporator when the compressor is stopped in the intermittent operation can be reduced. In addition, the temperature rise of the evaporator can be suppressed, and the energy loss during the intermittent operation can be reduced. Further, even when applied to a flammable refrigerant such as propane or isobutane, the amount of the refrigerant used is smaller than in the high-pressure system, and the safety of the device can be improved.

In the embodiments described above, a one-cylinder compressor is described as an example of the oscillating piston type compressor. However, the present invention is also applicable to a two-cylinder oscillating piston type compressor. Applicable. In addition, the horizontal type compressor has been described as an example, but in the case of the vertical type, the lower end of the drive shaft is immersed in the lubricating oil. The same applies because lubrication is possible.

[0045]

As described above in detail, according to the present invention, the lubricating oil is reliably supplied to the load supporting position of the sliding hole without impairing the compressed gas sealing property, so that the sliding member and the sliding hole can be connected. The wear of the piston can be reduced, and a swinging piston type compressor with high performance and high reliability can be provided.

Further, according to the present invention, the inside of the closed vessel is set at a pressure lower than the discharge pressure so as to reduce the amount of refrigerant used, to reduce the thickness and weight of the closed vessel, and to improve the gas sealing performance of the sliding member on the discharge port side. Highly reliable oscillating piston type that can ensure high performance without damage and can reliably supply lubricating oil to the load supporting position of the sliding hole, reducing wear on the sliding member and sliding hole A compressor is obtained.

According to the present invention, the crank angle at which the suction port is closed is reduced to increase the actual suction volume, and the effect of gas re-expansion in the clearance volume of the discharge port is reduced, so that the volumetric efficiency of the compressor is reduced. And the wear of the sliding member and the sliding hole is reduced without impairing the gas sealing performance of the sliding member on the discharge port side, and by promoting the supply of lubricating oil to the load supporting position of the sliding hole. And a high-performance and highly reliable oscillating piston compressor can be obtained.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a main part of a horizontal swinging piston type compressor according to a first embodiment of the present invention.

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

FIG. 3 is an operation explanatory diagram of the compression element of FIG. 1;

FIG. 4 is a polar diagram of a load vector acting on a sliding hole of a cylinder in the swinging piston type compressor of FIG. 1;

FIG. 5 is an explanatory view of a load acting position on an inner periphery of a sliding hole in the compressor.

FIG. 6 is a perspective view of a main part showing a structure around a sliding member in the compressor.

FIG. 7 is a plan view of a main part of a cylinder in a swinging piston type compressor according to a second embodiment of the present invention.

FIG. 8 is a longitudinal sectional view of a main part of a swinging piston type compressor according to a third embodiment of the present invention.

FIG. 9 is a sectional view taken along line BB of FIG. 8;

FIG. 10 is a polar diagram of a load vector acting on a sliding hole of a cylinder in the compressor.

FIG. 11 is an explanatory diagram of a load acting position on an inner periphery of a sliding hole in the compressor.

FIG. 12 is a configuration diagram of a refrigeration cycle of a refrigeration system according to a fourth embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Cylinder, 1a ... Cylindrical inner peripheral surface, 1b ... Sliding hole, 1
c: pump hole, 2: main bearing, 3 auxiliary bearing, 3a: suction port, 3b: discharge port, 3c: discharge chamber, 4: drive shaft, 4
a: Eccentric part, 4b: Oil supply piece, 5: Rotor, 6: Sealed container, 7: Stator, 8: Swing piston, 8a: Roller,
8b: vane, 10: sliding member, 11: compression chamber, 12:
Suction chamber, 13 suction pipe, 14 suction passage, 15 discharge cover, 16 discharge pipe, 17 lubricating oil, 18 suction fluid diode, 19 discharge fluid diode, 2
0 ... oil supply pipe, 21 ... swinging piston type compressor, 22 ...
Condenser, 23 expansion valve, 24 evaporator, 31 spiral groove, 32 oil pocket.

Continuing from the front page (72) Inventor Takeshi Kono 502 Kandachi-cho, Tsuchiura-shi, Ibaraki Pref. Machinery Research Laboratory, Hitachi, Ltd. (72) Inventor Akihiko Ishiyama 800, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Pref. (72) Inventor: Yugo Mukai 800 Futami, Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Prefecture F-term (Ref.)

Claims (8)

[Claims] 1. A cylinder having a cylindrical inner peripheral surface, an end plate closing both ends of the cylindrical inner peripheral surface of the cylinder, and a cylindrical member formed in a space surrounded by the cylinder and the end plate. A roller that revolves around the outer circumferential surface while maintaining a small gap with the cylindrical inner circumferential surface of the cylinder, a drive mechanism that gives the roller revolving motion, and a roller that protrudes radially from the cylindrical outer circumferential surface of the roller. A plate-shaped vane for partitioning the inside of the cylinder into a suction chamber communicating with a suction port and a compression chamber communicating with a discharge port, and having a central axis parallel to the central axis outside the cylindrical inner peripheral surface of the cylinder; A sliding hole into which the vane is inserted, and a cylindrical surface portion incorporated into two spaces formed between the sliding holes on both sides of the vane and slidably in contact with the sliding hole, and slidably on the flat portion of the vane. With a contacting flat part The sliding member on the suction port side and the sliding member on the discharge port side in a swinging piston type compressor provided in a closed container. A swinging piston type compressor characterized in that the circumferential length of the contact surface between the sliding piston and the sliding hole is shorter than the circumferential length. 2. The sliding piston type compressor according to claim 1, wherein the sliding member on the suction port side and the sliding are so arranged as to leave at least an angular range in which a load acting on a sliding hole is applied by the sliding member. The circumference of the contact surface with the hole is
An oscillating piston type compressor, wherein a circumferential length of a contact surface between the sliding member and the sliding hole on a discharge port side is shorter than a circumference thereof. 3. A cylinder having a cylindrical inner peripheral surface, an end plate for closing both ends of the cylindrical inner peripheral surface of the cylinder, and a cylindrical member formed in a space surrounded by the cylinder and the end plate. A roller that revolves around the outer circumferential surface while maintaining a small gap with the cylindrical inner circumferential surface of the cylinder, a drive mechanism that gives the roller a revolving motion, and a roller that protrudes radially from the cylindrical outer circumferential surface of the roller. A plate-shaped vane for partitioning the inside of the cylinder into a suction chamber communicating with a suction port and a compression chamber communicating with a discharge port, and having a central axis parallel to the central axis outside the cylindrical inner peripheral surface of the cylinder; A sliding hole into which the vane is inserted, and a cylindrical surface portion incorporated into two spaces formed between the sliding holes on both sides of the vane and slidably in contact with the sliding hole, and slidably on the flat portion of the vane. With a contacting flat part And a sliding piston type compressor having the two sliding members in a closed container, wherein the pressure in the closed container is lower than the discharge pressure, and the sliding hole on the suction port side and the cylindrical inner peripheral surface of the cylinder are provided. A swinging piston type compressor, wherein a corner formed is cut out to form a notch, and a suction port is formed so as to communicate with the notch. 4. The swinging piston type compressor according to claim 3, wherein the inside of the closed container is set to a suction pressure, and the notch is formed so as to leave at least an angle range in which a load acting on a sliding hole is applied by the sliding member. An oscillating piston compressor characterized by forming a part. 5. A swing piston type compressor according to claim 3, wherein a front end of said vane is inserted outside of a sliding hole of said cylinder and has a central axis parallel to its central axis. A hole was provided, the pump hole was immersed in lubricating oil stored in a closed container, and a cutout was formed by cutting out a corner on the suction port side formed by the slide hole and the pump hole. Oscillating piston compressor. 6. The swinging piston type compressor according to claim 3, wherein a suction pressure is applied to the inside of the sealed container, and a suction port side located between two notches to receive a load of the sliding member. Wherein the circumferential length of the sliding hole is set to be larger than the angle in the range of 50 ° to 120 °. 7. A cylinder having a cylindrical inner peripheral surface, an end plate for closing both ends of the cylindrical inner peripheral surface of the cylinder, and a cylindrical member formed in a space surrounded by the cylinder and the end plate. A roller that revolves around the outer circumferential surface while maintaining a small gap with the cylindrical inner circumferential surface of the cylinder, a drive mechanism that gives the roller revolving motion, and a roller that protrudes radially from the cylindrical outer circumferential surface of the roller. A plate-shaped vane for partitioning the inside of the cylinder into a suction chamber communicating with a suction port and a compression chamber communicating with a discharge port, and having a central axis parallel to the central axis outside the cylindrical inner peripheral surface of the cylinder; A sliding hole into which the vane is inserted, and a cylindrical surface portion incorporated into two spaces formed between the sliding holes on both sides of the vane and slidably in contact with the sliding hole, and slidably on the flat portion of the vane. With a contacting flat part In the swinging piston type compressor provided with two sliding members in a closed vessel, the inside of the closed vessel is set to discharge pressure, and a part of a vane tip side of a sliding hole on a suction port side is partially cut off. Oscillating piston type compressor. 8. A refrigeration / air-conditioning system using the oscillating piston type compressor according to any one of claims 1 to 8.