WO2018055824A1

WO2018055824A1 - Rolling cylinder-type displacement compressor

Info

Publication number: WO2018055824A1
Application number: PCT/JP2017/015581
Authority: WO
Inventors: 坪野　勇; 智弘小松; 尊矢口; 渡辺　誠二; 小川　健; 小谷　正直
Original assignee: 株式会社日立製作所
Priority date: 2016-09-20
Filing date: 2017-04-18
Publication date: 2018-03-29
Also published as: JP2019218861A

Abstract

A rolling cylinder-type displacement compressor is provided with: a cylindrical rolling cylinder having a cylinder groove; an orbiting piston having a slide groove; a stationary cylinder having a pin mechanism; a piston orbiting drive source, i.e. a drive source for the orbiting motion of the orbiting piston; a drive transmission section for connecting the orbiting piston and the piston orbiting drive source; a frame through which the drive transmission section passes; and a casing in which the orbiting piston, the rolling cylinder, the stationary cylinder, the piston orbiting drive source and the drive transmission section are housed; wherein the orbiting piston, the rolling cylinder and the stationary cylinder constitute a compression section; the orbiting piston relatively performs a reciprocating motion in the cylinder groove; and cylinder groove outer circumferential walls are provided at both end parts of the reciprocating motion in the cylinder groove. As a result, the seal integrity of an operating chamber in the rolling cylinder-type displacement compressor is improved and high compressor efficiency is achieved.

Description

Rolling cylinder positive displacement compressor

The present invention relates to a rolling cylinder type positive displacement compressor.

Rolling cylinder positive displacement compressors are devices that use geometrically unique trajectories (hypocycloids). When compressing a working fluid such as a refrigerant using this device, it is essential to prevent leakage of the working fluid in order to improve efficiency. In order to prevent leakage of the working fluid, it is also important to supply a sufficient amount of lubricating oil evenly to the sliding portion.

Patent Document 1 discloses a rolling cylinder type positive displacement compressor that has one compression part in which a turning piston is fitted in a rolling cylinder and compresses a working fluid by reciprocating movement of the turning piston, and lubricates the sliding part. What has enabled a sufficient supply of oil is disclosed.

International Publication No. 2016/067355

In the rolling cylinder positive displacement compressor described in Patent Document 1, since the cylinder groove extends to the outer peripheral surface of the rolling cylinder, the working chamber formed in the cylinder groove has a bottom surface portion (cylinder bottom end plate) of the cylinder groove. ), A leakage flow path that leads to the back space is generated, and there is room for improvement in that the compressor efficiency is reduced.

An object of the present invention is to achieve high compressor efficiency by improving the sealing performance of a working chamber in a rolling cylinder positive displacement compressor.

A rolling cylinder type positive displacement compressor according to the present invention includes a cylindrical rolling cylinder having a cylinder groove, a revolving piston having a slide groove, a stationary cylinder having a pin mechanism, and a piston that is a driving source for the revolving motion of the revolving piston. A casing that incorporates a turning drive source, a drive transmission part that connects the turning piston and the piston turning drive source, a frame through which the drive transmission part passes, a turning piston, a rolling cylinder, a stationary cylinder, a piston turning drive source, and a drive transmission part The revolving piston, the rolling cylinder, and the stationary cylinder constitute a compression portion, and the revolving piston relatively reciprocates in the cylinder groove, and the reciprocating motion in the cylinder groove has both ends. A cylinder groove outer peripheral wall is provided.

According to the present invention, in a rolling cylinder type positive displacement compressor, it is possible to improve the sealing performance of the working chamber and realize high compressor efficiency.

It is a longitudinal cross-sectional view which crosses the bypass valve and discharge flow path of RC compressor which concerns on Example 1. FIG. FIG. 2 is a cross-sectional view taken along the line AA in FIG. FIG. 3 is a cross-sectional view taken along the line BB in FIG. 1 is a perspective view illustrating a rolling cylinder of an RC compressor according to Embodiment 1. FIG. 1 is a perspective view showing a turning piston of an RC compressor according to Embodiment 1. FIG. It is a bottom view which shows the stationary cylinder which has a fixing pin concerning Example 1. FIG. 1 is an exploded perspective view illustrating a configuration of a compression unit of an RC compressor according to Embodiment 1. FIG. FIG. 2 is a flowchart illustrating a compression operation of the RC compressor according to the first embodiment with reference to a cross-sectional view slightly deviated from the BB cross section of FIG. 1 toward the revolving piston. FIG. 9 is an enlarged cross-sectional view illustrating an arrangement of the RC compressor according to the first embodiment at a crank angle of 0 deg in FIG. 8. FIG. 9 is an enlarged cross-sectional view illustrating an arrangement between a crank angle of 180 deg and 225 deg in FIG. 8 in which one working chamber of the RC compressor according to the first embodiment shifts from a compression stroke to a discharge stroke. It is an expanded sectional view of the P section of FIG. It is an expanded sectional view which shows the modification of FIG. FIG. 6 is an enlarged longitudinal sectional view showing a slide groove insertion portion of a pin slide mechanism of Embodiment 2. It is a perspective view which shows the slider of the pin slide mechanism of Example 2. FIG. It is a perspective view which shows the rolling cylinder of Example 3. FIG. It is a perspective view which shows the rolling cylinder of Example 4. FIG. It is a perspective view which shows the rolling cylinder of Example 5. FIG. FIG. 10 is a top view showing a rolling cylinder of Embodiment 5. It is a perspective view which shows the rolling cylinder of Example 6. FIG. FIG. 10 is a top view showing a rolling cylinder of Example 6. FIG. 10 is a perspective view showing a rolling cylinder of Example 7. FIG. 10 is a perspective view showing a rolling cylinder of Example 8. 1 is a top view showing a rolling cylinder of Embodiment 1. FIG. It is a top view which shows the turning piston of Example 1. 10 is a top view showing a rolling cylinder of Example 9. FIG. It is a top view which shows the turning piston of Example 9. FIG. 10 is a top view showing a rolling cylinder of Example 10. It is a top view which shows the turning piston of Example 10.

The present invention is a compressor having a typical configuration in which three main compression elements are a revolving piston that revolves, a rolling cylinder that rotates in conjunction with a stationary cylinder, and a stationary cylinder that incorporates them. The present invention relates to a rolling cylinder positive displacement compressor (hereinafter also referred to as “RC compressor”) that compresses a gas that is a working fluid by a compression element. Here, the working fluid includes not only non-condensable gases such as air but also refrigerants used in air conditioners and refrigerators.

Since the basic configuration of the RC compressor of the present invention is disclosed in Patent Document 1, this specification will be described focusing on the problems in the present invention and the means for solving them.

In particular, in order to keep the compression operation smoothly in order to avoid mechanism stoppage that occurs very frequently at the timing when the rotation axis of the piston that is the rotation axis of the revolving piston and the rotation axis of the cylinder that is the rotation axis of the rolling cylinder overlap, The present invention relates to a rolling cylinder type positive displacement compressor comprising: a rotation synchronization means for synchronizing the rotation speeds of a piston and a rolling cylinder; and a swing piston attitude restriction means by a rotation half means for regulating the rotation speed of the rotation piston to half of the rotation speed. .

These means control the posture of the swivel piston so that the cut shaft, which is the central axis of the piston cut surface of the swivel piston, always passes through the cylinder rotation axis, regardless of the swivel phase. Therefore, the orbiting piston does not hinder the passive rotation of the rolling cylinder having the diameter of the cylinder groove into which the orbiting piston is fitted, and does not stop the compression operation. For this reason, it is not necessary to provide a plurality of compression portions conventionally performed to avoid the mechanism stop described above, and to provide a rotation integration means for rotating the plurality of rolling cylinders integrally.

Therefore, it is possible to realize a rolling cylinder type positive displacement fluid machine having only one set of compression parts including one revolving piston and one rolling cylinder. As a result, it is optimal for a compressor having a small displacement volume even if it has a large capacity for use under a small capacity such as a refrigerator or high pressure such as carbon dioxide, and the compressor can be downsized. is there.

In the present embodiment, only one having a single compression unit is shown, but a compressor of a type having a plurality of compression units shown therein can also be realized. For example, two compression units may be used for the purpose of suppressing fluctuations in rotational torque. In this case, since the rolling cylinder need not be integrated, the assembling property of the compression portion is improved.

Next, the outline specifications of the rolling cylinder positive displacement compressor of the present invention will be described.

A rolling cylinder positive displacement compressor according to the present invention includes a swing piston, a rolling cylinder, a piston swing drive source, a drive transmission means, a rolling cylinder rotation support, a rotation synchronization means, a rotation half means, and a stationary cylinder. And a casing.

The orbiting piston rotates around the piston rotation axis, and revolves around the piston rotation axis parallel to the piston rotation axis with a turning radius E.

A rolling cylinder has a cylindrical shape that rotates around a cylinder rotation axis, and has a cylinder groove with a constant width, with a cylinder groove axis perpendicular to the cylinder rotation axis as a central axis and parallel to the cylinder rotation axis. Both side surfaces of the groove are parallel to the cylinder groove axis.

The piston turning drive source is a driving source for the turning motion of the turning piston.

The drive transmission means connects the turning piston and the piston turning drive source.

The rolling cylinder rotation support portion is a cylinder whose cylinder rotation axis is parallel to the piston rotation axis and is eccentric with respect to the piston rotation axis so that the cylinder rotation axis is fixedly arranged on the piston rotation path circle that is the rotation path of the piston rotation axis. The amount of eccentricity is arranged as E equal to the turning radius.

Rotation synchronization means synchronizes the amount of rotation of the piston, which is the amount of rotation of the revolving piston, with the amount of rotation of the rolling cylinder.

Rotation half means controls the piston rotation amount to half of the piston turning amount which is the turning angle amount of the turning piston.

The stationary cylinder and the rolling piston and the rolling cylinder are formed so as to form a compression portion that forms two working chambers by roughly sealing two spaces separated by fitting the swiveling piston into the cylinder groove and partitioning the cylinder groove. Contains the cylinder.

Casing has an oil storage part as well as a compression part.

The suction flow path and discharge flow path are connected to the stationary cylinder.

The suction flow path connects one working chamber whose volume is increased by the swiveling motion of the swivel piston, of the two working chambers, to the suction system.

The discharge channel connects the other working chamber, whose volume is reduced by the swiveling motion of the swivel piston, to the discharge system and serves as the discharge chamber.

The suction channel and the discharge channel have a period that does not lead to the suction system or the discharge system until the working chamber, which was the suction chamber immediately before the start of the decrease after the increase in volume, is transferred to the discharge chamber. It is arranged to be a compression chamber.

The rotation synchronizing means is provided with a piston cut surface, which is a flat surface of two constant intervals, with a cut axis perpendicular to the piston rotation axis as a central axis and parallel to the piston rotation axis, on the side surface of the orbiting piston that is in sliding contact with the two side surfaces of the cylinder groove. To achieve.

The rotation half means is a slide groove having a constant width parallel to the piston rotation axis with the slide axis orthogonal to the piston rotation axis as one of the two piston side end surfaces orthogonal to the piston rotation axis among the side surfaces of the orbiting piston. And a pin mechanism arranged on a rolling cylinder rotation support portion that is inserted into the slide groove with the pin axis as a central axis so that the pin axis parallel to the piston rotation axis is always perpendicular to the slide axis, arranged on the piston rotation locus circle It is comprised by the pin slide mechanism which consists of. Then, the pin shaft is arranged at a position on the piston turning locus circle rotated by the pin axis adjustment angle δ from a position opposed to the cylinder rotation shaft arranged on the piston turning locus circle by 180 degrees around the piston turning axis. At the same time, by rotating the slide shaft around the piston rotation axis from the normal direction of the cut shaft in the same rotation direction as the pin shaft adjustment angle by δ / 2 degrees, which is half of the pin shaft adjustment angle, Realize.

Hereinafter, the rolling cylinder type positive displacement compressor of the present invention will be described in detail with reference to the drawings as appropriate using a plurality of embodiments. In the drawings, common parts will be described using the same drawings. Moreover, the same code | symbol in the figure of each Example shows the same thing or an equivalent, and abbreviate | omits the overlapping description. Note that, in the portions other than those described as schematic illustrations, the dimensional ratios of the respective elements shown in the drawings indicate one embodiment. Therefore, the size relationship and angle of each dimension in the illustrated shape also indicate an embodiment. Further, the numbering with parentheses in the figure shows two embodiments depending on the presence / absence of the target part with parentheses. Further, specific dimension values are not particularly limited, but it is desirable that the outer diameter of the rolling cylinder type positive displacement compressor is in a range from 10 mm to 2000 mm.

FIG. 1 shows the overall configuration of the RC compressor of the first embodiment. In the description of this figure, the configuration described in Patent Document 1 is simplified.

As shown in the figure, the RC compressor is roughly composed of a compression unit, a motor 7 as a drive source, and an oil storage unit 125.

In this figure, the compression part, the motor 7, and the oil storage part 125 are arranged in order from the upper part in the casing constituted by the casing cylindrical part 8a, the casing upper cover 8b, and the casing lower cover 8c.

The compression unit includes a rolling cylinder 1, a turning piston 3, and a stationary cylinder 2 as components that directly act on the compressed working fluid. With respect to these materials, if the swiveling piston 3, the rolling cylinder 1 and the stationary cylinder 2 are all made of cast iron, the cost can be kept low. Alternatively, the rolling cylinder 1 may be made of an aluminum alloy, and the turning piston 3 and the stationary cylinder 2 may be made of cast iron. In this way, since the rolling cylinder 1 that rotates passively can be reduced in weight, it is possible to make it difficult for malfunctions to occur and smooth operation. Furthermore, if the revolving piston 3, the rolling cylinder 1 and the stationary cylinder 2 are all made of an aluminum alloy, the entire RC compressor can be reduced in weight.

The compression part has a structure in which the upper part is covered with a stationary cylinder 2 and the lower part is covered with a frame 4. The frame 4 is provided with a main bearing 24 including an upper main bearing 24a and a lower main bearing 24b. The crankshaft 6 is supported by the main bearing 24 in a rotatable state. The crankshaft 6 protrudes downward.

In the compression part, a working chamber is formed by the rolling cylinder 1, the turning piston 3, and the stationary cylinder 2. The working chamber is the suction chamber 95 or the compression chamber 100.

The stationary cylinder 2 is provided with a circular eccentric cylinder hole 2b having a cylinder rotation axis as a central axis. The stationary cylinder 2 has a cylinder outer peripheral groove 2m on the outer peripheral side surface thereof. From the upper surface of the stationary cylinder 2, a bypass hole 2e that penetrates to the eccentric cylinder hole 2b is provided. A bypass valve 22 is provided on the upper surface side of the stationary cylinder 2. This bypass valve 22 has a structure in which a valve plate is disposed on a valve seat and the valve plate is lightly pressed from above by a spring. As a result, the bypass valve 22 is a one-way valve that allows only the flow in the direction from the eccentric cylinder hole 2b to the upper part. A pin mechanism 5 is provided on the bottom surface of the eccentric cylinder hole 2b.

The compression section is provided with a suction passage 2s and a discharge hole 2d1. The suction passage 2s includes a suction groove 2s2 provided on the bottom surface of the eccentric cylinder hole 2b, and a suction hole 2s1 connected to the suction groove 2s2 from the upper surface of the stationary cylinder 2.

At the upper part of the stationary cylinder 2, a cylinder upper wall 2w is arranged so as to cover the inner side of the cylinder bolt 90 for attaching the stationary cylinder 2 to the frame 4. A discharge cover 230 is fixed on the upper surface of the cylinder upper wall 2w, and covers the discharge hole 2d1, the bypass hole 2e, and the like. And the upper wall groove | channel 2w1 which connects an inner peripheral part and an outer peripheral part is provided in the several places of the cylinder upper wall 2w.

The rolling cylinder 1 has a cylinder bottom end plate 1a that forms the bottom surface of the cylinder groove, and a cylinder groove outer peripheral wall 301. An eccentric shaft insertion hole 1 d is provided in the center of the bottom surface of the rolling cylinder 1.

The pin mechanism 5 is inserted into the slide groove 3b of the turning piston 3.

The swing bearing 23 is press-fitted into the swing bearing hole 3a (FIG. 2) provided in the swing piston 3. The eccentric shaft 6 a of the crankshaft 6 is inserted into the slewing bearing 23. The eccentric shaft 6a is connected to the turning piston 3 via the eccentric shaft insertion hole 1d. A shaft collar portion 6 c that is a large diameter portion is provided on the upper portion of the crankshaft 6. An eccentric portion including an eccentric shaft 6a and a shaft neck 6d having a smaller diameter than the eccentric shaft 6a is provided above the shaft collar portion 6c.

The motor 7 includes a stator 7b fixedly disposed on the casing cylindrical portion 8a and a rotor 7a fixedly disposed on the crankshaft 6. Here, the motor 7 is a piston turning drive source and also a shaft rotation drive source. The rotor 7a has a main balance 80 fixed at the top and a counter balance 82 fixed at the bottom. These serve to dynamically balance the unbalance of the compression element (slewing piston 3) that swirls in the compression operation. The stator 7b is provided with a stator winding 7b2.

The oil storage part 125 is an area surrounded by the casing cylindrical part 8a, the casing lower lid 8c, and the sub-frame 35.

The compression part is fixed to the casing cylindrical part 8a by welding or the like.

The oil pump 200 having a boosting capability is provided at the lower end of the crankshaft 6. The crankshaft 6 is provided with an oil supply vertical hole 6b (oil supply passage) penetrating the center in the central axis direction. Furthermore, the crankshaft 6 is provided with oil supply horizontal holes (oil supply sub horizontal hole 6g, oil supply lower main bearing hole 6f, oil supply upper main bearing hole 6e) connected to the sub bearing 25, the lower main bearing 24b, and the upper main bearing 24a. . The upper main bearing 24a is supplied with oil by an upper oil supply upper bearing hole 6e and an oil supply main shaft groove 6k.

A part of the oil discharged from the oil supply pump 200 enters the oil supply pump shaft chamber 150 through a gap around the pump connecting pipe 6z and is supplied to the auxiliary bearing 25.

The region surrounded by the crankshaft 6, the slewing bearing 23 and the slewing piston 3 is a shaft eccentric end space 115. The slewing bearing 23 is supplied with oil by the shaft eccentric end space 115 and the oil supply eccentric groove 6h.

The frame 4 is provided with a plurality of bed radiating grooves 4e serving as oil passages. A rotor cup 210 is tightly fixed to the lower surface of the frame 4 so as to cover the periphery of the rotor 7a. The oil that has passed through the bed radiation groove 4e flows into the back pressure chamber 110 and the bed back pressure chamber 110a, and is discharged from the oil discharge path 4x below the frame 4 to the outside of the rotor cup 210. .

On the outer periphery of the compression portion, there are gaps such as a cylinder outer peripheral gap 2g and a frame outer peripheral gap 4g, a cylinder outer peripheral groove 2m and a frame outer peripheral groove 4m, which serve as a flow path for the working fluid of the discharge pressure.

The suction pipe 50 introduces a working fluid from the outside to a compression section provided inside the casing 8. The discharge pipe 55 discharges the working fluid pressurized by the compression unit to the outside. The suction pipe 50 and the discharge pipe 55 are provided on the casing upper lid 8b. In addition, a hermetic terminal 220 is provided on the casing upper lid 8b. A motor wire 7b3 is connected to the hermetic terminal 220 so that electric power can be supplied to the stator winding 7b2 of the motor 7 from an external power source (not shown).

The working fluid introduced from the suction pipe 50 is pressurized in the compression section and discharged from the discharge pipe 55 to the outside.

Here, the flow of the working fluid will be described.

The working fluid introduced from the suction pipe 50 is compressed in the compression unit and blows upward from the discharge hole 2d1, the bypass hole 2e, and the like. Then, the working fluid once collides with the discharge cover 230. At this time, the oil contained in the working fluid adheres to the discharge cover 230 and is separated. The working fluid with a reduced amount of oil is blown out from the upper wall groove 2w1. The working fluid further collides with the inner wall of the casing cylindrical portion 8a, and the oil is separated again. Thereafter, the working fluid enters the casing upper chamber 120 and is discharged from the discharge pipe 55 provided in the casing upper lid 8b to the outside of the apparatus. Note that in the casing upper chamber 120, the flow rate of the working fluid decreases, so that a slight amount of remaining oil mist tends to settle, and the amount of oil contained in the working fluid becomes extremely small.

On the other hand, there is no main flow of working fluid below the compression part, but the cylinder outer peripheral gap 2g and the frame outer peripheral gap 4g which are outer peripheral gaps of the compression part, and the cylinder outer peripheral groove 2m which is the outer peripheral groove of the compression part, The working fluid of the discharge pressure flows through the frame outer peripheral groove 4m.
Thereby, the whole casing space including the lower part of a compression part becomes discharge pressure. That is, a high pressure chamber system is realized.

The auxiliary bearing 25 includes a ball 25a and a ball holder 25b that rotatably supports the ball 25a in all directions. After the lower part of the crankshaft 6 is inserted into the ball 25a and the ball 25a is mounted on the ball holder 25b, the ball holder 25b is fixedly disposed on the sub-frame 35 welded to the casing cylindrical portion 8a. Thereby, the auxiliary bearing 25 is configured to rotatably support the lower portion of the crankshaft 6.

Next, the flow of a part of oil flowing below the compression unit will be described.

The oil that flows out from the oil discharge path 4x to the lower side of the frame 4 comes out of the rotor cup 210 that covers the periphery of the rotor 7a and is firmly fixed to the lower surface of the frame 4. Then, it travels along the outer periphery of the rotor cup 210 and falls to the stator 7b, and further passes through a hole through which the stator winding 7b2 passes and the outer stator cut surface 7b1 to reach the space below the motor 7. Thereafter, a small amount passes through the sub-frame peripheral hole 35a and returns to the oil storage part 125 except that the small amount of oil passes through the sub-frame central hole 35b and is supplied to the inner and outer circumferences of the balls 25a of the sub-bearing 25.

Note that the RC compressor can be installed with the central axis of the cylindrical casing facing in the horizontal direction (lateral). In this case, there is no problem even if the central axis of the cylinder is inclined. However, in this case, it is necessary to adjust the arrangement of the sub-frame surrounding hole 35a and the sub-frame central hole 35b of the sub-frame 35, which is a partition of the oil storage part 125, so that an appropriate amount of lubricating oil stays in the oil storage part 125. There is.

In the following description, portions different from the configuration of each figure described in Patent Document 1 are described, and the same configuration as that described in Patent Document 1 is omitted.

FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1 (compression chamber forming portion).

FIG. 3 is a cross-sectional view taken along the line BB (a cross-sectional view in the gap between the swing piston and the rolling cylinder above the rolling cylinder).

Note that C1-C2-O-C3-C4 shown in FIGS. 2 and 3 is a portion corresponding to the longitudinal sectional view of FIG. 1, and FIG. 1 is a longitudinal sectional view passing through C1-C2-O-C3-C4. It is. Here, there are two C2 and C3 in FIG. 2 and FIG. 3, respectively, which means that in FIG. 1, between two C2 and between two C3 is omitted.

In FIG. 2, the rolling cylinder 1 is provided with a cylinder groove outer peripheral wall 301. The cylinder groove outer peripheral wall 301 is provided at both ends of the reciprocating motion of the revolving piston 3 in the cylinder groove 1c. In other words, the cylinder cylinder is provided with a cylinder groove outer peripheral wall 301 that partitions between the cylinder groove 1 c and a cylinder outer peripheral surface that is an outer peripheral surface of the rolling cylinder 1. For this reason, the suction hole is not provided in the cross section shown in FIG.

A cylinder outer peripheral groove 2m is provided in a part of the outer peripheral side surface of the stationary cylinder 2, and is arranged so as to communicate with the frame outer peripheral groove 4m provided in the lower frame.

In FIG. 3, the suction path 2s provided in the bottom surface of the eccentric cylinder hole 2b of the stationary cylinder 2 is actually indicated by a two-dot chain line. The suction path 2s includes a suction groove 2s2 provided on the bottom surface of the eccentric cylinder hole 2b, a suction hole 2s1 connected to the suction groove 2s2 from the upper surface of the stationary cylinder 2, and a suction groove refracting portion 2s2k. The suction groove 2 s 2 is provided at a position closer to the inside than the inner side surface of the cylinder groove outer peripheral wall 301. The suction groove refracting portion 2 s 2 k is provided outside the inner surface of the cylinder groove outer peripheral wall 301 and inside the outer surface of the cylinder groove outer peripheral wall 301. The suction groove 2s2 and the suction groove refracting portion 2s2k communicate with the upper surface portion of the stationary cylinder 2 through the suction hole 2s1.

A discharge groove 2d2 and a discharge hole 2d1 are provided on the bottom surface of the eccentric cylinder hole 2b. The discharge hole 2d1 is connected to the discharge groove 2d2 from the upper surface of the stationary cylinder 2. The discharge groove 2d2 and the discharge hole 2d1 constitute a discharge path 2d.

In summary, the suction path 2s (suction flow path) and the discharge path 2d (discharge flow path) are provided in the stationary cylinder 2 and face the working chamber of the compression unit closer to the central axis than the inner wall surface of the cylinder groove outer peripheral wall 301. It has a configuration.

FIG. 4 is a perspective view showing the rolling cylinder of this embodiment.

As shown in this figure, the rolling cylinder 1 is provided with a cylinder groove outer peripheral wall 301 up to the same height as the cylinder upper surface portion 1e. Thereby, all the sides of the working chamber are sealed.
An eccentric shaft insertion hole 1d is provided at the center of the bottom surface of the cylinder groove 1c.

Note that the dimension F indicates the depth of the cylinder groove 1c.

FIG. 23 is a top view showing an example in which the shape of the cylinder groove outer peripheral wall 301 of the rolling cylinder in FIG. 4 is limited.

23, the rolling cylinder 1 is provided with a uniform wall 1w having a uniform thickness as a cylinder groove outer peripheral wall. Further, the position of the piston eccentric cylindrical tip surface 3e when the revolving piston 3 approaches the uniform wall 1w on the left side in the figure in the cylinder groove 1c is indicated by a two-dot chain line. The minimum distance between the piston eccentric cylinder front end surface 3e and the right end of the eccentric shaft insertion hole 1d in the drawing is the minimum seal width, and is formed by the revolving piston 3 in the cylinder groove 1c by sufficiently securing the minimum seal width. The sealing of the working chamber can be ensured.

The rolling cylinder 1 includes a cylinder cylinder 1b having a cylindrical shape and having a cylinder groove 1c inside with the rolling axis as a central axis, and a cylinder bottom end plate 1a forming a bottom surface of the cylinder groove 1c. The cylinder groove 1c is provided in an open shape on the end surface of the cylinder column 1b on the side opposite to the cylinder bottom end plate, and is flat and parallel to each other with a constant width parallel to the rolling axis with the cylinder groove axis orthogonal to the rolling axis as the central axis. It has various sides. Further, the bottom surface of the cylinder groove 1c is parallel to each upper surface.

The cylinder groove 1c becomes a cylinder groove outer peripheral wall between the cylinder outer peripheral surface 1s as shown in FIG. Here, R which becomes processable is provided in the corner (small black circle location) of the cylinder groove 1c. For example, when the cylinder groove 1c is processed by an end mill, the radius of the corner (small black circle) R is set to be equal to or larger than the radius of the end mill. Further, as will be described later, when the cylinder column 1b and the cylinder bottom end plate 1a are separated, machining by wire cut which is electric discharge machining is also conceivable. In that case, the radius should be about the radius of the wire plus the gap removed by the discharge. On the other hand, in order to allow the swiveling piston 3 to fit into the cylinder groove 1c, the corner of the swiveling piston 3 (small white circle portion in FIG. 24) is shaped so as not to interfere with the corner portion (small black circle portion) of the cylinder groove 1c. Adjust. For example, R may be larger than R at the corner (small black circle) of the cylinder groove 1c.

The revolving piston 3 reciprocates in the cylinder groove 1c. For this reason, even when the turning piston 3 approaches the end of the cylinder groove 1c, the eccentric shaft insertion hole 1d is hidden by the turning piston 3, and the turning piston 3 is secured so as to secure a seal width (shown in FIG. 23 is the minimum seal width). It is necessary to increase the length of 3. When the length of the swiveling piston 3 is increased, it is necessary to increase the length of the cylinder groove 1c, and the diameter of the cylinder column 1b is increased. Therefore, since the diameter of the rolling cylinder 1 increases and the diameter of the stationary cylinder 2 into which the rolling cylinder 1 is incorporated increases, the diameter of the casing 8 increases and the RC compressor becomes larger in diameter.

In this embodiment, as shown in FIG. 1, the shaft neck 6d is provided so that the eccentric shaft insertion hole 1d passes through the shaft neck 6d having a smaller diameter than the eccentric shaft 6a. As a result, since the eccentric shaft insertion hole 1d can be made small while ensuring the seal width, there is an effect that an increase in the diameter of the RC compressor can be suppressed.

Further, in FIG. 3, most of the suction groove 2 s 2 is located at a position close to the inside from the side surface of the eccentric cylinder hole 2 b by the thickness of the outer peripheral wall of the cylinder groove (in this embodiment, the thickness of the uniform wall 1 w). Is provided. On the other hand, the suction groove refracting portion 2s2k is provided by refracting the end of the suction groove 2s2 so that the suction chamber 95 faces the suction groove 2s2 from the start of the suction stroke. Here, the suction groove refracting portion 2s2k is also provided so as not to face the discharge chamber 105 and to cross the uniform wall 1w. Further, a suction hole 2 s 1 is provided so as to connect the suction groove 2 s 2 or the suction groove refracting portion 2 s 2 k and the upper surface of the stationary cylinder 2. Here, the suction hole 2s1 is provided so as not to penetrate the bottom surface of the eccentric cylinder hole 2b. By providing such a suction groove 2s2 and a suction hole 2s1, a suction path 2s that is a section closer to the suction chamber of the suction flow path is formed.

As a result, the flow straddles the gap space between the working chamber formed inside the uniform wall 1w that is the outer circumferential wall of the cylinder groove and the cylinder outer circumferential surface 1s that is the gap area formed outside the uniform wall 1w and the side surface of the eccentric cylinder hole 2b. The road disappears. This improves the sealing performance between the space communicating with the gap space between the cylinder outer peripheral surface 1s and the side surface of the eccentric cylinder hole 2b and the suction pressure space such as the suction chamber 95 and the suction passage 2s (suction hole 2s1 and suction groove 2s2).

In this embodiment, the gap space between the cylinder outer peripheral surface 1s and the eccentric cylinder hole 2b side surface is connected to the back pressure chamber 110 held at the discharge pressure. Thereby, since the fluid of the discharge pressure from the back pressure chamber 110 can be prevented from leaking into the suction chamber 95, the volume efficiency and the compressor efficiency are improved.

Also, under over-compression conditions (for example, when the specific volume ratio is 2.2), the working fluid is discharged from the bypass hole 2e through the bypass valve 22. In this embodiment, the two bypass holes 2e are designed so that the bypass hole 2e faces the working chamber from the latter half of the suction stroke to the entire compression stroke and the first half of the discharge stroke. Thereby, there is an effect of improving the compressor efficiency by avoiding over-compression under over-compression conditions and reducing the discharge flow path resistance. In addition, since the suction stroke is included, liquid compression can be avoided, so that there is an effect of improving the reliability of the compressor.

FIG. 5 is a perspective view showing a revolving piston.

As shown in this figure, the swivel piston 3 has a structure in which two piston cut surfaces 3c that are parallel to the swivel axis and parallel to each other are provided on the side surface of a cylindrical material having a small thickness. The upper bottom surface of the swing piston 3 is a piston upper surface 3d, and the lower bottom surface of the swing piston 3 is a piston lower surface 3f. The piston upper surface 3d and the piston lower surface 3f are piston-side end surfaces and are parallel to each other. The piston upper surface 3d and the piston lower surface 3f are flat.

A slide groove 3b is provided on the piston upper surface 3d. The piston lower surface 3f is provided with a swivel bearing hole 3a having a circular cross section. A swing bearing 23 is press-fitted into the swing bearing hole 3a.

The slide groove 3b is formed with a depth communicating with the swivel bearing hole 3a. Thereby, the oil supply path to the slewing bearing 23 and the oil supply path to the slide groove 3b become common, and the oil supply system is simplified. This has the effect of reducing manufacturing costs. The slide groove 3b extends to the outer periphery of the piston cut surface 3c. Thereby, since the movement of the cutting tool during groove processing becomes uniform, there is an effect that the shape accuracy of the groove is improved.

In addition, the dimension H has shown the thickness of the turning piston 3. FIG.

In this figure, as shown by a two-dot chain line, a piston cut groove 3i connected to the slide groove 3b may be provided at the center of the piston cut surface 3c. Although not shown, a similar piston cut groove 3i may be provided on the opposite piston cut surface 3c. As a result, oil can be sufficiently supplied to the seal gap between the side surface of the cylinder groove 1c and the piston cut surface 3c in FIG. 4, so that there is an effect of further reducing internal leakage and friction.

The slide groove 3b also serves as an oil supply path to the piston cut surface 3c. By the way, in this embodiment, the slide shaft is set to the normal direction of the cut shaft (axis perpendicular to the swing bearing shaft). That is, the slide shaft is provided in a direction perpendicular to the two piston cut surfaces 3c parallel to the cut shaft. In this case, the pin shaft adjustment angle δ is set to 0 degree.

Furthermore, since the fixing pin 5s is inserted into the slide groove 3b, there is a risk of wear. Therefore, in order to reduce the risk of wear, a surface treatment for increasing the hardness of the side plane of the slide groove 3b may be performed. For example, if the revolving piston 3 is made of iron, carburizing and quenching or nitriding treatment can be considered. In the case of an aluminum alloy, alumite treatment or the like can be considered.

FIG. 24 is a top view showing the revolving piston.

As shown in the figure, when the swing piston 3 is viewed from above, the swing bearing hole 3a and the swing bearing 23 are partially visible in the slide groove 3b. The piston eccentric cylindrical tip surface 3e is one of the surfaces forming the working chamber.

The turning piston 3 is fitted in the cylinder groove 1c of FIG. When the piston eccentric cylindrical tip surface 3e comes into contact with the uniform wall 1w of FIG. 23 by the movement of the swiveling piston 3, the shape of the piston eccentric cylindrical tip surface 3e and the inner wall surface of the uniform wall 1w is as narrow as possible. It is desirable to have the same (curvature). In addition, the shape of the corner portion (small white circle portion in FIG. 24) of the orbiting piston 3 is adjusted so as not to interfere with the corner portion (small black circle portion in FIG. 23) of the cylinder groove 1c. For example, R may be larger than R at the corner of the cylinder groove 1c (small black circle in FIG. 23).

FIG. 6 is a bottom view of the stationary cylinder.

In this figure, a cylinder outer peripheral groove 2m provided on the outer peripheral side surface of the stationary cylinder 2, a suction path 2s composed of a suction hole 2s1, a suction groove 2s2, and a suction groove refracting portion 2s2k, and a discharge composed of a discharge hole 2d1 and a discharge groove 2d2. The arrangement of the path 2d and the pin mechanism 5 is clearly shown. Further, a bypass hole 2e that penetrates to the eccentric cylinder hole 2b is provided from the upper surface of the stationary cylinder 2. A bypass valve 22 is provided on the upper surface side of the stationary cylinder 2. From the bottom surface of the bypass valve 22, a bypass hole 2e penetrating to the eccentric cylinder hole 2b is provided near a portion corresponding to the radius of the inner surface of the cylinder groove outer peripheral wall 301 (FIG. 4). In this embodiment, there are two bypass holes 2e.

In addition, as shown in this figure, the distance between the pin shaft, which is the center of the pin mechanism 5, and the cylinder rotation shaft is twice the turning radius E.

FIG. 7 is a perspective view showing a state where the combination of the components of the compression unit and the crankshaft is developed.

In this figure, the arrangement of the cylinder outer circumferential groove 2m, the frame outer circumferential groove 4m, and the like, and the shapes of the eccentric shaft 6a, the shaft neck 6d, the shaft collar portion 6c, etc. constituting the upper end portion of the crankshaft 6 are clearly shown. Further, the relationship between the pin shaft, the piston rotation shaft, the shaft shaft (piston turning shaft), the cylinder rotation shaft, and each component is also clearly shown.

FIG. 8 is a view for explaining the compression operation using a cross section slightly shifted to the swivel piston side from the BB cross section of FIG. Here, in FIG. 8, the suction groove 2s2 immediately above the BB cross section is indicated by a broken line.

FIG. 9 is an enlarged view of the crank angle of 0 degree in FIG. This is the timing when the working chamber whose volume is changed from the discharge stroke to the suction stroke is zero and the working chamber whose maximum volume is changed from the suction stroke to the compression stroke coexist.

FIG. 10 is an enlarged view of the timing at which one working chamber shifts from the compression stroke to the discharge stroke when a bypass valve 22 described later does not operate, and is in a state between the crank angle of 180 degrees and 225 degrees in FIG. Is shown.

FIG. 11 is a vertical cross-sectional view of the pin mechanism mounting portion, and is an enlarged view of a portion P in FIG.

A cylindrical fixing pin 5s having a pin axis as a central axis is fixedly arranged on the bottom surface of the eccentric cylinder hole 2b (FIG. 7) to form a pin mechanism 5 (FIG. 7). By inserting the pin mechanism 5 into the slide groove 3b (FIG. 7), a pin slide mechanism is configured. The pin slide mechanism plays a role of defining the posture (cut axis direction) in accordance with the turning phase of the turning piston 3, and is a mechanism for smoothly continuing the compression operation of the RC compressor.

In FIG. 11, the fixing pin 5s is inserted into a hole penetrating from the upper surface of the stationary cylinder 2 to the eccentric cylinder hole 2b. The fixing pin 5s has a fixing pin flange portion 5s1, and the fixing pin flange portion 5s1 is fixed by using one or a plurality of pin fixing screws 5s8.
As a result, even if an impact load in a direction perpendicular to the axial direction is applied near the tip of the fixing pin 5s and a torque that squeezes the fixing pin 5s is applied, the screw is fixed at a location away from the pin shaft. The length of the arm is increased, and the opposing torque can be easily generated. Thereby, it is possible to avoid a risk that the fixing pin 5s drops off from the stationary cylinder 2, and a reliable compression operation can be continued.

Further, instead of the pin fixing screw 5s8, a pin fixing main body screw 5s9 may be provided on the upper part of the main body of the fixing pin 5s. In this case, there is an effect that the width of the diameter selection of the fixed pin flange portion 5s1 is widened and the degree of freedom in design is improved.

FIG. 12 is a modification of FIG.

In FIG. 12, the method of attaching the fixing pin 5s to the stationary cylinder 2 is changed to caulking instead of screwing shown in FIG.

As shown in FIG. 12, it is the same as FIG. 11 except that a fixed pin small flange portion 5s1 'having a reduced collar portion and a pin caulking hole 5s6 are provided. For this reason, description of common points is omitted.

In FIG. 12, the fixing of the fixing pin 5s is completed by inserting a press jig having a tapered tip into the pin caulking hole 5s6 and pushing it into the stationary cylinder 2. For this reason, there exists an effect of a reduction of assembly cost.

The fixing arrangement method of the fixing pins 5s constituting the pin mechanism 5 of this embodiment is a simple cylinder without providing the fixing pin flange portion 5s1 and the fixing pin small flange portion 5s1 'when the impact force applied to the fixing pin 5s is small. Possible shapes include press-fitting, shrink fitting, cold fitting, welding and adhesion. According to this method, the hole to be inserted does not need to be penetrated, so that the degree of freedom in design is improved and the manufacturing cost of the fixing pin 5s can be reduced.

Further, the pin mechanism 5 of the present embodiment may be provided with an oil supply hole (fixed pin vertical hole or fixed pin horizontal hole) having an outlet on the outer peripheral surface in the fixed pin 5s, but as shown by M part in FIG. The oil supply hole may not be provided. In this case, there is no need for drilling, which has the effect of reducing manufacturing costs.

The operation of the compression section is as shown in FIGS. 8, 9 and 10 (both cross sections slightly lower than the BB cross section of FIG. 1).

As shown in FIG. 8, as the rolling cylinder 1 having the cylinder groove 1c rotates, the revolving piston 3 relatively reciprocates in the cylinder groove 1c. In other words, the revolving piston 3 reciprocates relative to the cylinder groove 1c between the cylinder groove outer peripheral walls 301 at both ends thereof in the cylinder groove 1c.

Details are described in Patent Document 1 and therefore omitted.

In the present invention, since the cylinder groove outer peripheral wall 301 is provided, the arrangement of the suction passage 2s and the discharge passage 2d is different from that in Patent Document 1, but the operation of the compression portion and the flow of the working fluid in the compression portion are in principle. It's not different.

The difference between the oil flow and Patent Document 1 will be described.

The present invention is different in that an oil supply pump 200 is provided in the oil storage section 125 as shown in FIG. Other configurations are almost the same as those of Patent Document 1. Therefore, the detailed description regarding the flow of oil is abbreviate | omitted.

In the present embodiment, since the uniform wall 1w (FIG. 23), which is the outer circumferential wall of the cylinder groove, is provided at both ends of the cylinder groove 1c, the upper surface of the uniform wall 1w is also formed on the bottom surface of the eccentric cylinder hole 2b which is the opposing surface. Approach or slide. Therefore, the latter (the upper surface of the uniform wall 1w) among the upper surface gaps of the uniform wall 1w connected in series from the back pressure chamber 110 to the cylinder outer peripheral clearance (the clearance between the cylinder outer peripheral surface 1s and the inner peripheral surface of the eccentric cylinder hole 2b). (Gap) can be reduced.

As described above, by providing the uniform wall 1w which is the outer circumferential wall of the cylinder groove, all axial gaps surrounding the working chamber formed by the cylinder groove 1c partitioned by the revolving piston 3 can be reduced. As a result, the sealing performance of all the working chambers that become the suction chamber 95, the compression chamber 100, and the discharge chamber 105 is improved, and the volume efficiency and the compressor efficiency can be improved.

Also, the surface of the rolling cylinder 1 that can be urged to the stationary cylinder 2 can be limited to the upper surface of the rolling cylinder 1 because the rolling cylinder 1 has a cylindrical shape. Therefore, the gap between the upper surface of the cylinder groove outer peripheral wall (uniform wall 1w in this embodiment), which is a part of the upper surface of the rolling cylinder 1, can be reduced with the bottom surface of the eccentric shaft insertion hole 1d that is the opposite surface. As a result, even if the width of the cylinder groove outer peripheral wall (uniform wall 1w in the present embodiment) is reduced, the sealing performance is hardly deteriorated. Therefore, since the outer diameter of the rolling cylinder 1 can be reduced, there is an effect that an RC compressor that achieves both high compressor efficiency and a reduced diameter can be realized.

By the way, the orbiting piston 3 performs an extremely complicated relative movement with respect to the stationary cylinder 2 in which the rotation movement and the rotation movement overlap. Therefore, when the orbiting piston 3 is sandwiched between the bottom surface of the cylinder bottom end plate 1a and the eccentric cylinder hole 2b and the piston upper surface 3d (see FIG. 5) applies a biasing force between the bottom surface of the eccentric cylinder hole 2b, The frictional force acting on the piston upper surface 3d increases and changes in a complicated manner, and the turning speed and the rotation speed of the turning piston 3 vary greatly. As a result, the rotational movement of the rolling cylinder 1 that does not have a rotational drive source and rotates by the movement of the swiveling piston 3 also varies, which further increases the fluctuation of the movement of the swiveling piston 3. In this way, the compression operation is accompanied by extremely large irregular fluctuations, causing irregular collisions at each part of the compression part and extreme load fluctuations at the sliding part, increasing vibration noise and wear. , The efficiency of the compressor is reduced due to leakage and increased frictional force.

Therefore, there may be a case where the depth F (see FIG. 4) of the cylinder groove 1c is made larger than the thickness H (see FIG. 5) of the orbiting piston 3 (F> H). However, the difference (F−H) between the two, which is the size of the gap, is in the order of microns that can be sealed with an oil film.

As a result, even if the compression movable part is urged to the stationary cylinder 2, the urging force does not act on the piston upper surface 3d. Therefore, the frictional force acting on the piston upper surface 3d is small, and irregular fluctuations in the frictional force can be suppressed. As a result, the orbiting piston 3 moves smoothly. On the other hand, since the upper surface of the rolling cylinder 1 is urged against the bottom surface of the eccentric cylinder hole 2b, a frictional force is generated. The frictional force is caused by a simple rotational motion of the rolling cylinder 1, so As a result, the lubricity is improved, the friction coefficient is lowered, and the frictional force becomes extremely small. Furthermore, as described above, the revolving piston 3 that is the rotational drive source of the rolling cylinder 1 also moves smoothly, so that the above-described decrease in the friction coefficient is not hindered.

As a result, when F> H, the compression operation becomes extremely smooth, and it is possible to suppress irregular collisions that occur in each part of the compression unit represented by the pin mechanism, and to reduce the vibration noise and to improve reliability by suppressing wear. There is an effect of improving the sex. Furthermore, since extreme load fluctuations at the sliding part can be avoided, the oil film can be easily held, sealing and lubrication can be improved, leakage is reduced, and frictional force is reduced. There is an effect that improvement in efficiency can be realized.

Incidentally, the oil flowing into the back pressure chamber 110 is discharged from the oil discharge path 4x. Here, since most of the opening on the back pressure chamber 110 side of the oil discharge passage 4x is provided on the highest bed surface 4d of the back pressure chamber 110, the back pressure chamber 110 and the bed back pressure chamber 110a are oil of discharge pressure. Almost satisfied. Since the lower surface of the rolling cylinder 1 is almost at the same height as the bed surface 4d, the oil in the back pressure chamber 110 comes to the lower surface of the rolling cylinder 1 in a normal case.

Thus, the oil flows into a slight gap connecting the back pressure chamber 110 and the working chamber toward the suction chamber 95 and the compression chamber 100 having a pressure lower than the discharge pressure formed in the upper portion of the rolling cylinder 1. This gap includes a cylinder outer peripheral clearance (a clearance between the cylinder outer peripheral surface 1s and the inner peripheral surface of the eccentric cylinder hole 2b), an upper surface clearance of the uniform wall 1w connected in series therewith, and a piston lower surface 3f and a bottom surface of the cylinder groove 1c. There is a gap with the upper surface of a certain cylinder bottom end plate 1a. When oil flows into these gaps, the sealing performance and lubricity are improved, and the volume efficiency and the compressor efficiency are improved.

Incidentally, there may be a case where the back pressure chamber 110 side opening of the oil discharge passage 4x is provided at a low position of the back pressure chamber 110. In this case, since the oil hardly accumulates in the back pressure chamber 110, the oil does not contact the lower end of the rolling cylinder 1. As a result, oil agitation loss can be avoided. Therefore, in the case of an RC compressor in which the rolling cylinder 1 rotates at a high speed or the rotational speed of the rolling cylinder 1 is high at the rated operation (for example, the displacement volume). The compressor efficiency can be improved.

FIG. 13 is a longitudinal sectional view showing a slide groove insertion portion of the pin slide mechanism of the present embodiment, and is an enlarged view of an M portion in FIG. 11 or 12.

In FIG. 13, a slider flange 5b is provided at the tip (lower end) of the fixed pin 5s constituting the pin mechanism 5, and the slider 5a is rotatable between the fixed pin 5s and the slider flange 5b with respect to the pin axis. It is sandwiched and fitted into the slide groove 3b.

FIG. 14 is a perspective view showing a slider of the pin slide mechanism.

As shown in the figure, the slider 5a has a slider shaft hole 5a2 and a slider cut surface 5a1. The slider cut surface 5a1 is provided as two flat portions parallel to each other, and is a portion to be fitted into the slide groove 3b.

After inserting the slider flange 5b into the slider shaft hole 5a2 with a small gap (about 5 to 20 μm in diameter), the pin mechanism 5 is manufactured by press-fitting into the fixed pin 5s.

Thereby, the impact load applied to the pin mechanism is applied from the side surface of the slide groove 3b to the slider cut surface 5a1, and further from the slider shaft hole 5a2 to the shaft portion of the slider flange 5b. Since the former is between the flat surfaces and the latter is between the piston eccentric cylindrical peripheral surfaces, there is no load delivery involving a concentrated load. For this reason, since concentration of the load in the pin mechanism can be avoided, there is an effect that the risk of wear in the pin slide mechanism portion is reduced and the reliability is improved.

Further, in this embodiment, as shown in FIG. 13, the slider flange 5b is provided with a slider flange vertical hole 5b1 and a slider flange horizontal hole 5b2, and the slider shaft hole 5a2 and the slider from the shaft eccentric end space 115 filled with oil. An oil supply passage for supplying oil directly to the sliding portion of the flange 5b is provided. Thereby, there is an effect of further reducing the risk of wear at the pin slide mechanism and further improving the reliability of the RC compressor. Of course, this oil supply path is not necessary.

Note that the material of the slider 5a is generally cast iron or carbon steel, but may be a bearing material. For example, a carbon sintered material in which mainly carbon particles are baked and hardened may be used.

In FIG. 14, a slider groove 5a3 penetrating from one end of the slider cut surface 5a1 to the entire length of the other end is provided.

The slide groove 3b shown in FIG. 13 is normally filled with oil, and the pin mechanism 5 reciprocates therein. At this time, since the pin mechanism 5 is configured to partition the slide groove 3b (see FIG. 8), the pressure of the oil whose volume is reduced in the two slide groove spaces formed by partitioning is slightly reduced. Go up. Due to this pressure difference, oil flows into the slider groove 5a3.

Thereby, oil can be supplied to the slider cut surface 5a1 abundantly, so that the friction loss between the slider cut surface 5a1 and the sliding portion of the slide groove 3b is reduced, and the compressor efficiency is improved. Further, when the gap between the upper and lower sides of the slider 5a is small, there is also an effect that the increase of input electric power is suppressed by suppressing the pressure increase of the oil.

Incidentally, a plurality of slider grooves 5a3 may be provided on each slider cut surface 5a1 instead of one. Further, a non-penetrating slider groove 5a4 drawn on the slider cut surface 5a1 by a two-dot chain line may be used. In this case, it shall stop on the way from both ends. As a result, there is an effect that the pressurizing action works, the holding force of the oil film increases, and the risk of wear on the slider cut surface 5a1 and the slide groove 3b can be further reduced.

Further, two slider shaft oil supply holes 5a6 drawn by a two-dot chain line connecting the two slider tip surfaces 5a5 and the slider shaft hole 5a2 may be provided. As a result, the oil on the side whose volume is reduced among the two slide groove spaces formed by being partitioned by the pin mechanism 5 is slightly pressurized, so that the oil passes through the slider shaft oil supply hole 5a6 facing the space, A large amount flows into the slider shaft hole 5a2, and the shaft sliding portions of the slider shaft hole 5a2 and the slider flange 5b are reliably lubricated. As a result, there is an effect that the risk of wear at the shaft sliding portions of the slider shaft hole 5a2 and the slider flange 5b is further reduced, and the frictional force is reduced to improve the compressor efficiency.

FIG. 15 is a perspective view showing the rolling cylinder of this embodiment.

In this figure, a cylinder annular recess 1n is provided on the cylinder outer peripheral surface 1s. Thereby, the cylinder annular convex part 310 is formed. Since the configuration other than this is the same as that of the first embodiment, the description regarding the same portion is omitted.

Since the cylinder outer peripheral surface 1s rotates opposite to the inner peripheral surface of the eccentric cylinder hole 2b (FIG. 7), the rolling cylinder 1 can be regarded as a shaft portion that is supported by the bearing of the eccentric cylinder hole 2b and rotates. . In the present invention, since the cylinder groove outer peripheral wall 301 is provided, the sliding area of the shaft portion of the rolling cylinder 1 (the area of the cylinder outer peripheral surface 1s) is twice the cross-sectional area of the cylinder groove 1c, and the cylinder groove outer peripheral wall 301 is. It increases by the total area increase due to the increase in thickness. The friction loss of the bearing portion generally increases as the sliding area of the shaft increases. For this reason, if the cylinder groove outer peripheral wall 301 is simply provided, an increase in the area of the cylinder outer peripheral surface 1s causes an adverse effect of an increase in friction loss in the eccentric cylinder hole 2b, and the performance improvement amount is slightly reduced.

Therefore, in this embodiment, the cylinder annular recess 1n is provided on the cylinder outer peripheral surface 1s to reduce the sliding area of the bearing portion, and the cylinder annular recess 1n is provided closer to the center of the cylinder outer peripheral surface 1s. The bearing support state does not change, and friction loss can be reduced. As a result, an increase in the sliding area, which is one of the adverse effects of the cylinder groove outer peripheral wall 301, can be avoided, so that the compressor efficiency can be brought closer to the improvement of the compressor efficiency by the inherent leakage suppression that can be realized by the cylinder groove outer peripheral wall 301. There is an effect that can be done.

FIG. 16 is a perspective view showing the rolling cylinder of this embodiment.

In this figure, the back pressure chamber 110 (see FIG. 1) and the cylinder annular recess 1n are provided below the cylinder annular recess 310 formed by providing the cylinder annular recess 1n near the center of the cylinder outer peripheral surface 1s. A plurality of rolling outer peripheral lower end recessed portions 1v that connect the two are provided at approximately equal intervals.
Thereby, the oil of the discharge pressure is further stored in the back pressure chamber 110 up to the lower end height of the rolling outer periphery lower end recess 1v (not shown). Other than this, since it is the same as that of the third embodiment, the description regarding the same part is omitted.

Since there is a slight leakage channel from the cylinder annular recess 1n to the low-pressure working chamber via the upper surface of the cylinder annular projection 310, the pressure of the cylinder annular recess 1n is the discharge pressure back pressure chamber. Slightly lower than 110. Therefore, the oil of the discharge pressure of the back pressure chamber 110 flows into the cylinder annular recess 1n through the rolling outer peripheral lower end recess 1v. Further, it flows into the working chamber through the upper surface of the cylinder annular convex portion and the upper surface of the rolling cylinder 1. As a result, since lubrication is performed on sliding portions such as the cylinder annular convex portion and the upper surface of the rolling cylinder 1, the friction coefficient is reduced and the friction loss is reduced.

On the other hand, when the discharge pressure oil flows into the low-pressure working chamber, there are problems such as substantial leakage due to the working fluid dissolved in the oil and heating of the working fluid, but the order is negligible because the flow rate is extremely small. It becomes.

Therefore, overall, since the power to be supplied is reduced, there is an effect that the compressor efficiency is improved.

FIG. 17 is a perspective view showing the rolling cylinder of this embodiment. FIG. 18 is a top view showing the rolling cylinder of this embodiment.

As shown in these drawings, in this embodiment, a cut surface 1q and a cut surface oil supply hole 1p connected to the cut surface 1q are provided on the cylinder outer peripheral surface 1s. Since other than this is the same as in the first to fourth embodiments, the description regarding the same parts is omitted.

Here, the other end of the cut surface oil supply hole 1p is opened to the side surface of the cylinder groove 1c so as to always face the slide groove 3b (see FIG. 7) of the turning piston 3 inserted into the cylinder groove 1c. That is, as shown in FIG. 18, even when the orbiting piston 3 moves to both ends of the cylinder groove 1c, it is provided so that the cylinder side opening of the cut surface oil supply hole 1p faces the slide groove 3b.
The cut surface 1q is provided at a position that is an angle θ (about 60 degrees in this embodiment) of 90 degrees or less from the center of the cylinder groove outer peripheral wall 301 in the rotation direction of the rolling cylinder 1 (the same direction as the turning motion).

Here, as described in the third embodiment, the rolling cylinder 1 provided with the cylinder groove outer peripheral wall 301 can be regarded as a shaft portion that is supported by the bearing of the eccentric cylinder hole 2b and rotates.
Further, when the cylinder groove outer peripheral wall 301 is provided, the rolling cylinder 1 is parallel to the direction of the cylinder groove 1c due to the pressure difference between the working fluids in the two working chambers formed by the rotating piston 3 partitioning the cylinder groove 1c. Receive strong power. This is because the pressure applied to the inner surface of the cylinder groove outer peripheral wall 301 differs between the two working chambers, so that the force from the low pressure working chamber to the high pressure working chamber acts on the rolling cylinder 1. Accordingly, the rolling cylinder 1 can be regarded as a shaft that receives a load in a direction from the low pressure side working chamber to the high pressure side working chamber, and the eccentric cylinder hole 2b can be regarded as a journal sliding bearing that supports the shaft.

As a result, as apparent from the theory of the journal sliding bearing, the rolling is performed at a position slightly rotated from the center of the cylinder groove outer peripheral wall 301 forming the high pressure side working chamber in the rotational direction of the rolling cylinder 1 (the same direction as the turning motion). Due to the eccentricity of the cylinder 1, a minimal portion of the journal slide bearing gap is generated.

Furthermore, from the theory of journal sliding bearings, the vicinity of the bearing clearance minimum portion on the front side in the rotational direction of the rolling cylinder 1 with the minimum bearing clearance is the lower pressure region than the surroundings. The position of the minimum bearing clearance is determined by the magnitude of the load, the rotational speed of the rolling cylinder 1 and the viscosity of the oil, but at least from the load direction (the direction of the cylinder groove 1c) from the rotational direction of the rolling cylinder 1 90 degrees. It can also be seen that the position is small.

By the way, when the oil in the journal slide bearing is accumulated, the oil temperature rises, the viscosity is lowered, the bearing gap becomes substantially zero, and the possibility of seizure increases. For this reason, in journal slide bearings, the oil supply passage is opened from the bearing gap minimum part where the pressure is lower than the surroundings to the position near the rotational direction, so that oil is supplied to the bearing gap abundantly and seizure of the bearing part is avoided. And improve reliability.

In this embodiment, the same countermeasure is taken on the cylinder outer peripheral surface 1s of the rolling cylinder 1 this time. That is, the cut surface 1q is provided at a position where the angle θ is 90 degrees or less (about 60 degrees in the present embodiment) from the center of the cylinder groove outer peripheral wall 301 where the pressure is lower than the surroundings, and the discharge surface oil is always applied thereto. A cut surface oil supply hole 1p connected to the filled slide groove 3b is provided. That is, the cut surface 1q is a cylinder oil supply groove, and the cut surface oil supply hole 1p is a cylinder oil supply groove (also simply referred to as “oil supply hole”). And since it is connected with the slide groove 3b, it is a slide groove communication path.

As a result, oil can be sufficiently supplied to the gap between the cylinder outer peripheral surface 1s and the eccentric shaft insertion hole 1d inner peripheral surface via the cut surface 1q, so the cylinder outer peripheral surface 1s and the eccentric shaft insertion hole 1d inner peripheral surface. This has the effect of avoiding seizing and improving reliability. Further, since a stable oil film can be formed in the gap between the cylinder outer peripheral surface 1s and the eccentric shaft insertion hole 1d inner peripheral surface, the rotational motion of the rolling cylinder 1 can be stabilized. Therefore, since the friction loss of this journal sliding bearing part can be reduced, there is an effect that the compressor efficiency is improved.

Here, the cut surface 1q may be provided at a position of 90 degrees from the center of the cylinder groove outer peripheral wall 301. In this case, the cut surface 1q is installed closer to the rotational direction from the bearing gap minimum portion under any operating conditions, and therefore, it is possible to install without considering operating conditions. There is.

Also, the cylinder oil groove may be a cut surface oil groove 1r instead of the cut surface oil hole 1p. At this time, the oil in the back pressure chamber 110 is supplied to the cut surface 1q. In this case, it is not necessary to install a cylinder oil supply groove on the revolving piston 3, and it can be installed simply by extending the cut surface 1q to the lower end of the cylinder outer peripheral surface 1s, so that the processing cost can be reduced.

FIG. 19 is a perspective view showing the rolling cylinder of this embodiment. FIG. 20 is a top view showing the rolling cylinder of this embodiment. Here, the cylinder outer peripheral surface 1s is schematically shown. As in the fifth embodiment, the cylinder outer circumferential surface 1s may be provided with the cylinder annular recess 1n, the cut surface 1q and the cut surface oil supply hole 1p, and the cut surface 1q and the cut surface oil supply groove 1r.

The cylinder bottom end plate 1a and the cylinder column 1b of the rolling cylinder 1 shown in FIG. 4 are formed as a flat separate cylinder bottom end plate 1a ′ and a cylindrical separate cylinder column 1b ′, and the cylinder shaft and the separate cylinder bottom end. Since it is the same as that of Example 1 thru | or 9 except fixing with the end plate screw 1f so that the center axis | shaft of board 1a 'may match, description regarding the same location is abbreviate | omitted.

The separate cylinder column 1b 'has a through hole that becomes the cylinder groove 1c.

According to the present embodiment, it is possible to flatten the finishing process of the cylinder bottom end plate 1a, and it is possible to improve the accuracy and reduce the cost.

When the separate cylinder bottom end plate 1a ′ and the separate cylinder column 1b ′ are not separated, the bottom corner of the cylinder groove 1c is always provided with R, so that the lower corner of the swiveling piston 3 (piston cut surface) 3c and the boundary portion between the piston eccentric cylindrical tip surface 3e and the piston lower surface 3f) must be removed by corners such as chamfering in order to avoid interference. As a result, a gap is formed between the lower corner of the swiveling piston 3 and the bottom corner of the cylinder groove 1c, which becomes a leakage flow path connecting the two working chambers, leading to a reduction in compressor efficiency. It was.

In the present embodiment, the bottom corner portion of the cylinder groove 1c is formed by combining the separate cylinder bottom end plate 1a 'and the separate cylinder column 1b', so that no R portion is generated. Therefore, the lower corner portion of the orbiting piston 3 does not need to be removed, and a leak passage at the lower corner portion of the orbiting piston 3 is not formed. Therefore, an RC compressor in which the cylinder bottom end plate 1a and the cylinder column 1b are integrated is used. This also has the effect of improving the compressor efficiency.

It is also conceivable that the outer radius of the separate cylinder bottom end plate 1a 'is made smaller than the outer radius of the separate cylinder column 1b'. In other words, the outer diameter of the separate cylinder bottom end plate 1a 'is made smaller than the outer diameter of the separate cylinder column 1b'. In this case, when the screw is fixed by the end plate screw 1f, the center alignment of the separate cylinder bottom end plate 1a ′ and the separate cylinder column 1b ′ can allow an error of only the radius difference, and thus the manufacturing cost can be reduced. There is.

Furthermore, the separate cylinder column 1b 'and the separate cylinder bottom end plate 1a' may be welded or bonded without being screwed.

FIG. 21 is a perspective view showing the rolling cylinder of this embodiment.

In this figure, the cylinder cylinder to be separated is a separate cylinder cylinder 1b ″ with a side recess having a cylinder annular recess 1n at the lower end of the outer peripheral surface, and the diameter of the cylinder bottom end plate to be separated is the cylinder cylinder. Except for the separate cylinder large-diameter bottom end plate 1a ″ matched with the outermost diameter, it is the same as that of the third embodiment, and therefore, the description regarding the same parts is omitted.

Since the cylinder annular recess 1n can be formed by cutting the lower end side of the outer peripheral surface of the cylinder cylinder, there is an effect of reducing the processing cost.

FIG. 22 is a perspective view showing the rolling cylinder of the present embodiment.

In this figure, the cylinder cylinder to be separated is a separate cylinder cylinder 1b'ｂ '' with a central recess that is provided with a cylinder annular recess 1n on the outer peripheral surface center side, and the diameter of the cylinder bottom end plate to be separated is the cylinder Since it is the same as that of Example 3 except it is set as the separate cylinder small diameter bottom end plate 1a 'ａ' 'made smaller than the outermost diameter of a cylinder, explanation about the same portion is omitted.

When fixed with the end plate screw 1f, the centering of the separate cylinder small-diameter bottom end plate 1a '' 'and the separate cylinder cylinder 1b' '' with a central recess allows for an error of only the radius difference, making assembly easier. There is an effect of reducing the manufacturing cost.

Further, since the cylinder annular convex portions are provided at the upper end and the lower end of the height range in which the cylinder groove 1c exists, a force (bearing support force) that opposes the horizontal gas load due to the compression of the working fluid that the rolling cylinder 1 receives. Is divided into two equal parts from the two cylindrical annular projections. Therefore, since the maximum bearing support force can be reduced, there is an effect that reliability is improved. Further, the friction coefficient at the cylinder annular convex portion is reduced, and the friction loss can be reduced. Therefore, the compressor efficiency can be improved.

FIG. 25 is a top view showing the rolling cylinder of this embodiment. FIG. 26 is a top view showing the orbiting piston of the present embodiment.

In these drawings, the two tip surfaces of the orbiting piston 3 become piston cylindrical tip surfaces 3x having the same central axis, and correspondingly, the cylinder groove outer peripheral wall 301 becomes thicker toward both ends in the circumferential direction. Except for the non-uniform wall 1x that increases, this is the same as in the first to eighth embodiments, and thus the description of the same portion is omitted.

Rotating piston 3 may be formed by processing piston cut surface 3c after processing piston cylinder tip surface 3x which is the tip surface coaxial with slewing bearing hole 3a. Therefore, since the turning bearing hole 3a and the piston cylindrical tip surface 3x can be machined with high coaxiality by lathe machining by the same chucking, there is an effect that the manufacturing cost is reduced.

Further, since a large gas load is applied to the cylinder groove outer peripheral wall 301, high rigidity is required. In the present embodiment, the cylinder groove outer peripheral wall 301 is a non-uniform wall 1x whose thickness increases as it goes to both ends in the circumferential direction, so that the base of the wall is thick. Therefore, since the cylinder groove outer peripheral wall 301 has high rigidity, deformation due to gas load is suppressed, interference between the inner surface of the cylinder groove outer peripheral wall 301 and the tip surface of the turning piston 3, and the outer surface of the cylinder groove outer peripheral wall 301 and the eccentric cylinder hole 2b. There is an effect that the risk of interference with the inner peripheral surface can be reduced and the reliability is improved. Further, by suppressing the deformation of the outer surface of the cylinder groove outer peripheral wall 301, the friction coefficient with the inner peripheral surface of the eccentric cylinder hole 2b is reduced, and the friction loss can be reduced. Therefore, the compressor efficiency can be improved.
On the other hand, a case where the rigidity increase of the cylinder groove outer peripheral wall 301 is used to reduce the thickness of the cylinder groove outer peripheral wall 301 is also conceivable. Thereby, since the outer diameter of the rolling cylinder 1 can be reduced, there is an effect that the diameter of the RC compressor can be reduced.

FIG. 27 is a top view showing the rolling cylinder. FIG. 28 is a top view showing the orbiting piston.

In these figures, the two tip surfaces of the orbiting piston 3 are piston semi-cylindrical tip surfaces 3y each having a cylindrical surface whose diameter is the distance between the two piston cut surfaces 3c. Since it is the same as that of the ninth embodiment except that the thickness is further increased as compared with the non-uniform wall 1x of the ninth embodiment as it goes to both ends in the circumferential direction, the description on the same parts is omitted. .

The revolving piston 3 reciprocates relative to the cylinder groove 1c of the rolling cylinder 1. On the other hand, an eccentric shaft insertion hole 1d communicating with the back pressure chamber is opened at the center of the bottom (cylinder bottom end plate) of the cylinder groove 1c. Therefore, even when the orbiting piston 3 approaches one side in the cylinder groove 1c, a seal portion must be provided between the tip surface of the orbiting piston 3 and the eccentric shaft insertion hole 1d.

In the present embodiment, the seal width of the portion requiring the installation of the seal portion is set to the almost same minimum seal width (see FIG. 27). Accordingly, it can be considered that leakage between the working chamber and the back pressure chamber 110 is effectively suppressed with a minimum seal width. This is due to the fact that the connection position between the piston cut surface 3c of the revolving piston 3 and the piston tip surface is shifted to the piston rotation shaft side.

As a result, since the cylinder groove outer peripheral wall 301 can be formed into a long hole forming wall 1y whose thickness increases greatly toward both ends in the circumferential direction, the base of the wall has a very thick form. Therefore, since the cylinder groove outer peripheral wall 301 is very high in rigidity, deformation due to gas load is completely suppressed, and interference between the inner surface of the cylinder groove outer peripheral wall 301 and the tip surface of the swiveling piston 3 and the outer surface of the cylinder groove outer peripheral wall 301 The risk of interference with the inner peripheral surface of the eccentric cylinder hole 2b can be reduced with extremely high accuracy, and the reliability is greatly improved. Further, since the deformation of the outer surface of the cylinder groove outer peripheral wall 301 is extremely suppressed, the friction coefficient with the inner peripheral surface of the eccentric cylinder hole 2b becomes very small, and the friction loss can be further reduced. Therefore, there is an effect that the compressor efficiency can be further improved.

On the other hand, a case where the increased rigidity of the cylinder groove outer peripheral wall 301 is used to reduce the thickness of the cylinder groove outer peripheral wall 301 is also conceivable. Thereby, since the outer diameter of the rolling cylinder 1 can be further reduced, there is an effect that the RC compressor can be further reduced in diameter.

Furthermore, it becomes possible to process the cylinder groove 1c with an end mill whose diameter is the distance between the two piston cut surfaces 3c. Thereby, there exists an effect that processing cost reduces.

According to the present invention, in the rolling cylinder positive displacement compressor, the sealing performance of the working chamber can be improved, and high compressor efficiency can be realized. Further, it is possible to suppress an increase in the diameter of the compression element accompanying the improvement in the sealing performance of the working chamber, and to achieve both high compressor efficiency and downsizing.

According to the present invention, it is possible to block the leakage flow path that communicates with the back space of the cylinder bottom end plate via the outer periphery of the cylinder bottom end plate of the rolling cylinder, so that the sealing performance of the working chamber can be improved and high compressor efficiency can be achieved. realizable. In addition, the leakage flow path can be blocked without increasing the size, and high compression efficiency and downsizing can be realized.

1: rolling cylinder, 1a: cylinder bottom end plate, 1a ′: separate cylinder bottom end plate, 1b: cylinder cylinder, 1c: cylinder groove, 1d: eccentric shaft insertion hole, 1f: end plate screw, 1n: cylinder annular recess 1p: Cut surface oil supply hole, 1q: Cut surface, 1r: Cut surface oil supply groove, 1s: Cylinder outer peripheral surface, 1v: Rolling outer peripheral lower end recess, 1w: Uniform wall, 1x: Non-uniform wall, 1y: Slot formation Wall, 2: Static cylinder, 2a: Cylinder mounting surface, 2b: Eccentric cylinder hole, 2d: Discharge passage, 2e: Bypass hole, 2g: Cylinder outer circumferential clearance, 2m: Cylinder outer circumferential groove, 2s: Suction passage, 2w: Upper cylinder Wall, 3: slewing piston, 3a: slewing bearing hole, 3b: slide groove, 3c: piston cut surface, 3d: piston upper surface, 3f: piston lower surface, 3e: piston eccentric cylindrical tip surface, i: piston cut groove, 3x: piston cylindrical tip surface, 3y: piston semi-cylindrical tip surface, 4: frame, 4a: frame mounting surface, 4b: main bearing hole, 4c: collar receiving surface, 4c1: collar receiving notch, 4d: Bed surface, 4e: Bed radiation groove, 4g: Frame outer periphery clearance, 4m: Frame outer periphery groove, 4x: Oil discharge passage, 5: Pin mechanism, 5a: Slider, 5a1: Slider cut surface, 5a2: Slider shaft hole, 5a5: Slider tip surface, 5a6: Slider shaft oil supply hole, 5b: Slider flange, 5b1: Slider flange vertical hole, 5b2: Slider flange horizontal hole, 5c: Slider rolling element, 5s: Fixed pin, 5s1: Fixed pin flange, 5s1 ' : Fixed pin small flange, 5s3: fixed pin vertical hole, 5s5: fixed pin side hole, 5s6: pin caulking hole, 5s8: pin fixing screw, 5 9: Pin fixing body screw, 6: Crankshaft, 6a: Eccentric shaft, 6b: Lubricating vertical hole, 6c: Shaft collar, 6d: Shaft neck, 6e: Upper oiled main bearing hole, 6f: Lower oiled main bearing hole, 6g : Oil supply sub horizontal hole, 6h: Oil supply eccentric groove, 6k: Oil supply main shaft groove, 6z: Pump connection pipe, 7: Motor, 7a: Rotor, 7b: Stator, 7b1: Stator cut surface, 7b2: Stator winding, 7b3: Motor Wire, 8: casing, 8a: casing cylindrical portion, 8b: casing upper lid, 8c: casing lower lid, 22: bypass valve, 23: slewing bearing, 24: main bearing, 24a: upper main bearing, 24b: lower main bearing 25: Sub bearing, 25a: Ball, 25b: Ball holder, 35: Sub frame, 35a: Sub frame peripheral hole, 35b: Sub frame central hole, 50: Suction pipe, 55 : Discharge pipe, 80: Main balance, 82: Counter balance, 85: Discontinuous familiar film, 86: Continuous familiar film, 90: Cylinder bolt, 95: Suction chamber, 100: Compression chamber, 105: Discharge chamber, 110 : Back pressure chamber, 110a: bed back pressure chamber, 115: shaft eccentric end space, 120: casing upper chamber, 125: oil storage section, 150: oil pump shaft chamber, 200: oil pump, 301: cylinder groove outer peripheral wall, 310: Cylinder annular convex part.

Claims

A cylindrical rolling cylinder having a cylinder groove;
A swivel piston having a slide groove;
A stationary cylinder having a pin mechanism;
A piston turning drive source which is a drive source of the turning motion of the turning piston;
A drive transmission unit connecting the revolving piston and the piston revolving drive source;
A frame through which the drive transmission portion passes;
The revolving piston, the rolling cylinder, the stationary cylinder, the piston revolving drive source, and a casing containing the drive transmission unit,
The swiveling piston, the rolling cylinder and the stationary cylinder constitute a compression part,
The orbiting piston relatively reciprocates in the cylinder groove,
A rolling cylinder type positive displacement compressor in which cylinder groove outer peripheral walls are provided at both ends of the reciprocating motion in the cylinder groove.
The rolling cylinder positive displacement compressor according to claim 1, wherein a depth of the cylinder groove is larger than a thickness of the orbiting piston.
The compression part has a suction channel and a discharge channel,
The said suction flow path and the said discharge flow path are provided in the said stationary cylinder, It is the structure which faces the working chamber of the said compression part nearer to a center axis than the inner wall face of the said cylinder groove outer peripheral wall. The rolling cylinder type positive displacement compressor as described.
The rolling cylinder type positive displacement compressor according to any one of claims 1 to 3, further comprising an oil supply passage that connects a cylinder outer peripheral surface of the rolling cylinder and the cylinder groove.
The cylinder outer peripheral surface is provided with a cylinder oil groove that is continuous with the oil supply passage,
The cylinder oil supply groove is provided at a position rotated from the center of the outer peripheral wall of the cylinder groove by an angle of 90 degrees or less in the rolling cylinder rotation direction that is the rotation direction of the rolling cylinder, which is the same direction as the turning motion. The rolling cylinder type positive displacement compressor according to claim 4.
The rolling cylinder positive displacement compressor according to claim 4 or 5, wherein a cylinder annular recess is provided on the outer peripheral surface of the cylinder.
The rolling cylinder has a configuration in which a separate cylinder bottom end plate and a separate cylinder column are integrated,
The rolling cylinder type positive displacement compressor according to any one of claims 1 to 6, wherein the separate cylinder column has a through hole serving as the cylinder groove.
The rolling cylinder positive displacement compressor according to claim 7, wherein an outer peripheral diameter of the separate cylinder bottom end plate is smaller than an outer peripheral diameter of the separate cylinder column.