JP6294974B2 - Rolling cylinder positive displacement compressor - Google Patents

Description

  The present invention is a compressor having three main compression elements, a revolving piston that revolves, a rolling cylinder that rotates with the revolving piston, and a stationary cylinder that incorporates the revolving piston. The present invention relates to a rolling cylinder type positive displacement compressor that compresses a certain gas.

  Japanese Patent Application Laid-Open No. 2010-185358 (Patent Document 1) discloses a means for solving the problem of locking of the pump operation in a rolling cylinder type positive displacement pump. In the positive displacement pump described in Patent Document 1, the working fluid is liquid oil, and the rotation of the swing piston and the rotation of the rolling cylinder are maintained, and the swing speed of the swing piston is defined as twice the rotation speed of the rolling cylinder. A rotation defining means is provided. The rotation defining means includes rotation synchronization means for synchronizing the rotation of the turning piston and the rotation of the rolling cylinder, and piston rotation defining means for defining the turning speed of the turning piston to be twice the rotation speed. The rotation synchronization means is configured by providing a flat side portion that is in sliding contact with the two side surfaces of the pump groove on the revolving piston. Further, the piston rotation defining means is configured to fit the position-fixed cylinder into the guide groove.

  On the other hand, JP, 2011-17300, A (patent documents 2) is a conventional example of a rolling cylinder type positive displacement compressor assumed to be used for a refrigerating cycle device. Patent Document 2 includes two suction / discharge mechanisms for sucking and discharging refrigerant by reciprocating a piston in a piston chamber provided in a rotating cylinder, and the cylinder is pivoted by a back pressure of the discharge pressure. A compressor is disclosed that biases in the direction and eliminates the need for clearance management between the partition member and the end face of the cylinder. In this conventional example, the compression operation is smoothly continued by combining another rolling cylinder compressor having different rotational phases.

JP 2010-185358 A JP 2011-17300 A

  In the positive displacement pump described in Patent Document 1, the piston rotation defining means (pin mechanism) has a configuration in which a position-fixed column (fixed pin) is fitted in the guide groove. A load acts on the pin mechanism only when the compression mechanism deviates from the normal operation. For this reason, the load applied to the pin mechanism is often a shocking irregular load, and reliable lubrication is always necessary. In the case of a positive displacement pump, since the working fluid is liquid oil having lubricity, reliable lubrication can be realized only by arranging a pin mechanism in the discharge flow path.

  The compressor described in Patent Document 2 is different from the method using the rotation defining means described in Patent Document 1. In other words, two compression mechanisms having different rotational phases are essential. For this reason, the volume of the whole compressor becomes large and the number of parts also increases. Therefore, there is a limit to improvement in terms of downsizing the compressor. Furthermore, it is necessary to assemble to strictly define the rotational phase difference between the two compression mechanisms, which causes a problem of deterioration in assembly.

  When the pin mechanism described in Patent Document 1 is applied to a compressor that employs a rolling cylinder system, it is necessary to provide oil supply means for the pin mechanism in order to use the working fluid as a gas. Conventionally, there is no example in which the pin mechanism is applied to a compressor.

  An object of the present invention is to sufficiently supply lubricating oil to a pin mechanism and improve the reliability of the pin mechanism when the pin mechanism is applied to a rolling cylinder positive displacement compressor.

  A rolling cylinder positive displacement compressor of the present invention includes a crankshaft having an eccentric shaft with a shaft axis as a rotation center, a frame that supports the crankshaft, a rotation drive source that applies a rotation drive torque to the crankshaft, and an operation A compression section that sucks, compresses and discharges fluid, and an oil storage section. The compression section rotates a rolling cylinder having a cylinder groove, a swinging piston slidably accommodated in the cylinder groove, and a rolling cylinder. A space surrounded by the rolling cylinder, the swiveling piston, and the stationary cylinder in accordance with the rotation of the rolling cylinder and the swiveling piston, and a suction chamber, a compression chamber, and a discharge chamber. The eccentric shaft has a different center line from the shaft axis and the swivel piston is It is arranged so as to be able to rotate around the center line of the shaft, revolves according to the rotation of the crankshaft, the fixed cylinder having a center line different from the shaft axis is attached to the eccentric cylinder hole of the stationary cylinder, and the swing piston slides The fixed pin has a structure that is slidably fitted in the slide groove. The intersection of the bottom surface of the eccentric cylinder hole and the center line of the fixed pin, the bottom surface of the eccentric cylinder hole, and the rolling cylinder Arranged so that the midpoint of the line connecting the intersection with the center line coincides with the intersection of the bottom surface of the eccentric cylinder hole and the center line of the shaft axis, and these three center lines are parallel to each other As a result, the rotation of the swing piston and the rotation of the rolling cylinder are synchronized, and the rotation angular speed of the swing piston is adjusted to half of the rotation angular speed of the crankshaft. Pressure oil reservoir portion is configured to be equal to the pressure in the discharge chamber, and, by providing a Aburaren passage connecting the oil storage portion and the slide groove, and supplies the lubricating oil of the oil storage portion to the fixing pin and the slide groove.

  According to the present invention, when a pin mechanism is applied to a rolling cylinder positive displacement compressor, lubricating oil can be sufficiently supplied to the pin mechanism, and the reliability of the pin mechanism can be improved.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view across a bypass valve and a discharge passage of a rolling cylinder positive displacement compressor according to a first embodiment. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. 1 is a perspective view illustrating a rolling cylinder of a rolling cylinder type positive displacement compressor according to Embodiment 1. FIG. 1 is a perspective view showing a turning piston of a rolling cylinder positive displacement compressor according to Embodiment 1. FIG. It is a bottom view which shows the stationary cylinder which attached the fixing pin of the rolling cylinder type positive displacement compressor which concerns on Example 1. FIG. 1 is a perspective view showing a frame of a rolling cylinder type positive displacement compressor according to Embodiment 1. FIG. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an exploded perspective view illustrating a configuration of a compression unit of a rolling cylinder type positive displacement compressor according to a first embodiment. It is a flowchart shown using the figure seen from the cross section slightly lower than the BB cross section of FIG. 1 about the compression operation of the rolling cylinder type positive displacement compressor which concerns on Example 1. FIG. FIG. 10 is an enlarged cross-sectional view showing details of the arrangement at a crank angle of 0 deg in FIG. 9. FIG. 10 is an enlarged cross-sectional view illustrating an arrangement between a crank angle of 180 deg and 225 deg in FIG. 9 in which one working chamber of the rolling cylinder type positive displacement compressor according to the first embodiment shifts from a compression stroke to a discharge stroke. FIG. 4 is an enlarged cross-sectional view showing a part M in FIG. 3. It is OG sectional drawing of FIG. 1 is an enlarged cross-sectional view schematically showing the vicinity of a surface of a rolling cylinder or a revolving piston of a rolling cylinder type positive displacement compressor according to Embodiment 1. FIG. 6 is an enlarged cross-sectional view schematically showing the vicinity of the surface of a rolling cylinder or a revolving piston of a rolling cylinder type positive displacement compressor according to Embodiment 2. FIG. FIG. 6 is an enlarged cross-sectional view showing a portion corresponding to part M in FIG. 3 in a rolling cylinder type positive displacement compressor according to a third embodiment. It is OG sectional drawing of FIG. FIG. 6 is an enlarged longitudinal sectional view showing a portion corresponding to a portion P in FIG. 1 in a rolling cylinder type positive displacement compressor according to a fourth embodiment. FIG. 7 is an enlarged longitudinal sectional view showing a portion corresponding to a P portion of FIG. 1 in a rolling cylinder type positive displacement compressor according to a fifth embodiment. FIG. 10 is an enlarged perspective view showing a slider in a rolling cylinder positive displacement compressor according to a fifth embodiment. FIG. 10 is an enlarged longitudinal sectional view showing a portion corresponding to a portion Q in FIG. 1 in a rolling cylinder type positive displacement compressor according to a sixth embodiment. FIG. 10 is a perspective view showing a rolling cylinder with a cylindrical end of a rolling cylinder type positive displacement compressor according to a sixth embodiment.

  The present invention is a compressor having three main compression elements, a revolving piston that revolves, a rolling cylinder that rotates with the revolving piston, and a stationary cylinder that incorporates the revolving piston. The present invention relates to a rolling cylinder type positive displacement compressor that compresses a certain gas. In particular, in order to continue the compression operation smoothly, a rotation synchronization means for synchronizing the rotation speeds of the swing piston and the rolling cylinder and a rotation half means for regulating the rotation speed of the swing piston to half of the rotation speed are provided. The present invention relates to a rolling cylinder positive displacement compressor.

  The rotation synchronization means and the rotation half means are realized by a pin slide mechanism that uses a slide groove of the swing piston and a pin mechanism fixedly disposed on the stationary cylinder. Here, the pressure in the oil storage section is configured to be equal to the pressure in the discharge chamber. Thereby, the lubricating oil of an oil storage part can be supplied to a pin slide mechanism.

  Examples of the working fluid used in the present invention include air and refrigerant.

  Hereinafter, a rolling cylinder type positive displacement compressor and its effects according to embodiments of the present invention will be described.

  In the rolling cylinder type positive displacement compressor, the oil communication passage may be a separately provided pipe, but it is desirable that the oil communication passage is a vertical oil supply hole penetrating the crankshaft and the eccentric shaft, and a hole communicating from the oil storage portion to the slide groove. . This eliminates the need to add piping for refueling. Further, by providing the crankshaft or the like with a lateral hole that communicates with the vertical oil supply hole, oil supply to the bearing or the like is facilitated.

  In the rolling cylinder positive displacement compressor, the orbiting piston has two piston cut surfaces that are parallel and flat with each other, and the cylinder groove of the rolling cylinder has two inner side surfaces that are parallel and flat with each other. It is desirable to have a configuration in which the two piston cut surfaces are slidable between the two inner side surface portions. This ensures synchronization of the rotation speeds of the swing piston and the rolling cylinder.

  Since the rolling cylinder positive displacement compressor is intended for compression, there are a suction chamber for suction pressure and a compression chamber and a discharge chamber for increasing the pressure to the discharge pressure in the vicinity of the pin mechanism. Therefore, in order to reliably supply oil to the pin mechanism, it is necessary to supply at least oil having a discharge pressure. By implementing this, the reliability of the pin mechanism can be improved. However, since the vicinity of the pin mechanism is the discharge pressure that is the maximum pressure in the compressor, oil of the discharge pressure enters the gap near the pin mechanism. However, there arises a problem that the gap is enlarged.

  As a result, the axial clearance between the orbiting piston and the stationary cylinder, which is the clearance closest to the pin mechanism, is also enlarged. Since this gap serves as a seal portion between the compression chamber or the discharge chamber and the suction chamber, leakage increases as the gap increases. Similarly, the axial clearance between adjacent rolling cylinders and stationary cylinders also increases and leakage increases. Furthermore, since the working fluid is a gas, the amount of leakage increases. Furthermore, since the purpose is compression, the pressure difference between the suction chamber, the compression chamber, and the discharge chamber increases, and the amount of leakage further increases. As a result, there arises a problem that the compressor efficiency is greatly reduced.

  When compressing a gas that is a compressible fluid, it is desirable to provide a back pressure support means from the viewpoint of improving the sealing performance.

  In the rolling cylinder type positive displacement compressor, a back pressure chamber is provided between the rolling cylinder and the frame, and the stationary cylinder has a back pressure DC path communicating the compression chamber and the back pressure chamber. It is desirable that the pressure in the back pressure chamber be an intermediate pressure between the pressure in the suction chamber and the pressure in the discharge chamber. This is the back pressure support means. Thereby, since a differential pressure is generated between the discharge chamber and the back pressure chamber, oil can be reliably supplied to a main bearing and a slewing bearing described later.

  In the rolling cylinder positive displacement compressor, it is preferable that a back pressure valve is attached to a flow path that connects the compression chamber and the back pressure chamber. Thereby, since the setting of the pressure difference between the compression chamber and the back pressure chamber is performed by the back pressure valve, the inner diameter of the flow path can be increased. For this reason, the drill blade used in the production of the flow path can be made thick, processing becomes easy, and processing costs can be reduced. Further, since the swing piston and the rolling cylinder can be urged at a pressure close to the minimum necessary pressure for urging the stationary cylinder, the sliding loss caused by the urging can be reduced. This also contributes to an improvement in compressor efficiency.

  In the rolling cylinder type positive displacement compressor, one compression section can be provided. In other words, it is not necessary to have a configuration in which another compression unit having a different rotation phase is overlapped. Thereby, a compact rolling cylinder type positive displacement compressor can be obtained.

  In the rolling cylinder positive displacement compressor, it is desirable that the compression unit, the rotational drive source, and the oil storage unit are arranged in this order and are connected by a crankshaft. Thereby, circulation of lubricating oil can be facilitated and the number of parts can be reduced.

  In the rolling cylinder type positive displacement compressor, it is desirable that the rolling cylinder has an eccentric shaft insertion hole and the swing piston closes the eccentric shaft insertion hole. Thereby, the airtightness of a compression part can be ensured.

  In the rolling cylinder positive displacement compressor, it is desirable that a shaft neck having a smaller diameter than the eccentric shaft is provided between the eccentric shaft and the rotation shaft of the crankshaft. Thereby, the diameter of the eccentric shaft insertion hole can be reduced, and the diameter of the compressor can be reduced.

  In the rolling cylinder type positive displacement compressor, it is desirable that a bypass hole having a bypass valve which is a one-way valve is provided at the bottom of the eccentric cylinder hole of the stationary cylinder. Thereby, the pressure of a compression chamber can be maintained appropriately.

  In the rolling cylinder positive displacement compressor, the rolling cylinder includes a rolling cylinder having a cylinder groove and a rolling end plate, and the diameter of the rolling end plate is preferably larger than the diameter of the rolling cylinder. Thereby, the sealing performance of a compression part can be improved.

  In the rolling cylinder type positive displacement compressor, the rolling cylinder is a rolling cylinder having a cylinder groove, and has a configuration in which a rolling end plate, which is a separate body from the rolling cylinder, is stacked on the rolling cylinder. It is desirable to make the diameter larger than the diameter of the rolling cylinder. Thereby, processing of a rolling cylinder and a rolling end plate becomes easy.

  In the rolling cylinder positive displacement compressor, it is desirable that a step is provided between the bottom of the cylinder groove and the end plate front surface on the cylinder groove side of the rolling end plate. Thereby, the sealing performance of a compression part can be improved.

  In the rolling cylinder type positive displacement compressor, the rolling cylinder may include a rolling cylinder having a cylinder groove and a rolling cylinder end portion having a diameter equal to that of the rolling cylinder. Thereby, the diameter of a compression part can be made small and a sealing performance can be improved.

  In the rolling cylinder positive displacement compressor, it is desirable that a conformable film is provided on at least one of the rolling cylinder and the orbiting piston. Thereby, even if the dimensional accuracy of the swivel piston is relaxed, high performance can be realized, so that the manufacturing cost can be reduced.

  Hereinafter, the rolling cylinder 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 each drawing, common portions will be described using the same drawing. Moreover, the same code | symbol in the figure of each Example shows the same thing or an equivalent, and the overlapping description is abbreviate | omitted. Further, in the following description, there are cases where the expression including the direction of the upper surface or the lower surface is included in the state of being installed in the vertical direction in the figure, but the actual installation is not limited to the direction expressed here. .

  A rolling cylinder type positive displacement compressor (hereinafter abbreviated as RC compressor) according to Embodiment 1 will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of an RC compressor, and is a longitudinal sectional view passing through C1-C2-O-C3 in a transverse sectional view (FIGS. 2 and 3) along AA or BB shown in the drawing. Here, C2 has two places in FIGS. 2 and 3, which means that the space between the two places C2 is omitted. 2 and 3 are an AA sectional view (compression chamber forming portion) and a BB sectional view (axial gap portion between a stationary cylinder, a turning piston, and a rolling cylinder) in FIG. Here, in FIG. 3, the suction groove 2 s 2 immediately above the BB cross section is illustrated by a two-dot chain line. 4 and 5 are perspective views of the rolling cylinder and the revolving piston, respectively. FIG. 6 is a bottom view of the stationary cylinder, and FIG. 7 is a perspective view of the frame. And the perspective view explaining the assembly of the compression element part which united these and the crankshaft is FIG. FIG. 9 is an explanatory view of the compression operation using a section slightly lower than the section BB of FIG. Here, in FIG. 9, the suction groove 2s2 immediately above the BB cross section is shown by a broken line. FIG. 10 is an enlarged view of the crank angle of 0 degrees 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. 11 is an enlarged view of the timing at which one working chamber shifts from the compression stroke to the discharge stroke, and shows a state between the crank angle of 180 degrees and 225 degrees in FIG. 12 is an enlarged cross-sectional view of a portion M in FIG. 3 in which the back pressure flow path is arranged, and FIG. 13 is a longitudinal cross-sectional view taken along line OG in FIG. Finally, FIG. 14 is an enlarged cross-sectional view near the surface of the rolling cylinder or pivot piston.

  First, after explaining the whole structure except the inside of the compression part of RC compressor, the flow of the working fluid and oil in parts other than the compression part will be explained. Next, the configuration of the compression unit and the flow of working fluid and oil will be described in detail.

  Initially, the whole structure except the inside of a compression part is demonstrated using FIG. The compression part is covered with a stationary cylinder 2 at the upper part and a frame 4 at the lower part, and the crankshaft 6 that is rotatably supported by a main bearing 24 comprising an upper main bearing 24a and a lower main bearing 24b provided on the frame 4 projects downward. Yes. The crankshaft 6 is provided with a motor 7 while the compression portion is fixed to the chamber cylindrical portion 8a by welding or the like. The motor 7 includes a stator 7b fixedly disposed on the chamber cylindrical portion 8a and a rotor 7a fixedly disposed on the crankshaft 6. Here, a main balance 80 is fixed to the upper portion of the rotor 7a, and a counter balance 82 is fixed to the lower portion. These have the role of dynamically balancing the unbalance of the compression element (swinging piston 3) that swirls in the compression operation together with the shaft balance 81 fixedly arranged on the crankshaft 6 described in the explanation of the compression unit.

  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 lower frame 35 welded to the chamber cylindrical portion 8a. Thus, the auxiliary bearing 25 rotatably supports the lower part of the crankshaft 6. An oil supply piece 6 x is press-fitted into the lower end of the crankshaft 6. The crankshaft 6 is provided with an oil supply vertical hole 6b penetrating the center in the central axis direction. Further, the crankshaft 6 is provided with oil supply horizontal holes (oil supply sub horizontal hole 6g, oil supply lower main horizontal hole 6f, oil supply upper main horizontal hole 6e) connected to the sub bearing 25, the lower main bearing 24b, and the upper main bearing 24a.

  In the present specification, the “center line” refers to a straight line passing through the center of a member having a columnar shape or a cylindrical shape. Hereinafter, “center axis” or “axis” may be used to mean “center line”.

  A chamber lower lid 8c is attached to the lower portion of the chamber cylindrical portion 8a by welding. Here, an oil storage portion 125 is formed in which oil is sealed at an appropriate stage of assembling the RC compressor, and the oil is stored in the vicinity of the lower chamber lid 8c which is the lowermost portion. The oil supply piece 6x is always immersed in the oil in the oil storage section 125. The oil in the oil storage part 125 is sent to each part through the oil supply piece 6x, the oil supply vertical hole 6b of the crankshaft 6, and the oil supply horizontal hole.

  Further, a chamber upper lid 8b is welded to the upper portion of the chamber cylindrical portion 8a to form a sealed chamber 8 (described in FIGS. 12 and 13) together with the chamber lower lid 8c. A suction pipe 50 for introducing a working fluid from the outside to the compression section provided inside the sealed chamber 8 is provided in the chamber upper lid 8b. Further, the chamber upper cover 8b includes a discharge pipe 55 that discharges the working fluid pressurized by the compression unit to the outside of the RC compressor, an external power supply line (not shown) for supplying electric power to the motor 7, and a stator 7b. A hermetic terminal 220 to which the motor wire 7b3 connected to is connected is provided.

  Next, the flow of the working fluid that is a gas will be described. The working fluid enters the compression section through the suction pipe 50, where the pressure is increased by the compression operation of the compression element described in detail later. The pressurized working fluid is discharged into the RC compressor from the discharge flow path 2d on the side surface of the compression section, and the inside of the chamber 8 is set as the discharge pressure. Thereafter, the working fluid is directed to the discharge pipe 55 provided in the chamber upper lid 8b, and therefore flows to the upper side of the compression unit, and is finally discharged from the discharge pipe 55 to the outside of the RC compressor.

  Next, the flow of oil will be described. As described above, the oil storage portion 125 is connected to each bearing by the oil supply pipe 6x, the oil supply vertical hole 6b, the oil supply horizontal hole (the oil supply sub horizontal hole 6g, the oil lower main horizontal hole 6f, and the oil upper main horizontal hole 6e) that are always immersed in the oil storage portion 125. An oil supply passage is provided. As described above, since the pressure in the oil storage part 125 is the discharge pressure, the oil in the oil storage part 125 also becomes the discharge pressure. As will be described in detail later in the description of the compression section, a back pressure chamber 110 is provided to hold the oil outlet side from the main bearing 24 and the slewing bearing 23 at a back pressure that is intermediate between the discharge pressure and the suction pressure. Oil is supplied to the main bearing 24 and the slewing bearing 23 by a differential pressure between the pressure and the back pressure. Further, the auxiliary bearing 25 is supplied with oil by centrifugal oil supply from the oil supply auxiliary lateral hole 6g, and the oil after lubrication returns directly to the oil storage part 125.

  On the other hand, the oil that has lubricated the main bearing 24 and the slewing bearing 23 and entered the back pressure chamber 110 has lubricated and sealed each part in the compression part, and then moved from the discharge flow path 2d to the inside of the RC compressor together with the working fluid. Discharged. Here, of the oil supply passages in the compression section, only the oil supply passage that passes through the back pressure chamber 110 has been described, but the present invention is not limited thereto, and other oil supply passages also exist. However, the last is discharged together with the working fluid from the discharge flow path 2d into the RC compressor. These will be described in detail later in the description of the compression unit.

  When the oil discharged from the discharge flow path 2d into the RC compressor together with the working fluid collides with the inner wall of the chamber cylindrical portion 8a, most of the oil adheres to the inner wall due to viscosity and is separated from the working fluid. The oil separated into the inner wall of the chamber cylindrical portion 8a flows down to the compression unit lower space through the oil flow lowering cut surface 4g. Then, the oil flows down to the stator lower space through the holes through which the stator cut surface 7b1 and the stator winding 7b2 are passed, and finally, the oil is stored through the oil dropping peripheral hole 35a and the oil dropping central hole 35b of the lower frame 35. Return to part 125. Here, the oil passing through the dropping center hole 35 b also serves as oil supply to the sub bearing 25. In particular, oil is supplied to the gap between the ball 25a and the ball holder 25b.

  Next, the configuration of the compression unit will be described in detail with reference to FIGS.

  First, the frame 4 serving as the base of the compression unit will be described with reference to FIG. The frame 4 has a configuration in which a frame mounting surface 4a for attaching the stationary cylinder 2 later is used as an upper surface, and a main bearing hole 4b is provided in the center. An upper main bearing 24a and a lower main bearing 24b (see FIG. 1) are press-fitted into the main bearing hole 4b to form a main bearing 24 that rotatably supports the crankshaft 6. A shaft thrust surface 4c is provided around the upper surface of the main bearing hole 4b, and a shaft thrust surface groove 4c1 serving as an outlet passage for oil lubricating the main bearing 24 is provided at one or a plurality of locations. And the bed surface 4d which mounts the rolling cylinder 1 is provided in the position surrounding the shaft thrust surface 4c. The bed surface 4d is provided with a bed radiating groove 4e and a bed outer peripheral groove 4f serving as an oil passage. On the other hand, on the outer periphery of the frame 4, as described above, the oil flow lower cut surface 4g which is an oil passage separated from the working fluid is provided.

  Next, the turning piston 3 will be described with reference to FIG. The orbiting piston 3 has a configuration in which an orbiting bearing hole 3a is provided at the center. The slewing bearing 23 is press-fitted into the slewing bearing hole 3a. Further, two piston cut surfaces 3c that are parallel to each other and two cylindrical peripheral surfaces 3e that are offset from each other are provided on the side surface of the orbiting piston 3. Further, a piston upper surface 3d and a piston lower surface 3f, which are flat surfaces parallel to each other, are provided above and below. Among these, the piston upper surface 3d is provided with a slide groove 3b that intersects with the piston rotation axis that is the central axis of the slewing bearing 23 and that has a slide axis that is orthogonal to the piston cut surface 3c as a central axis. This slide groove 3b is set to a depth communicating with the swivel bearing hole 3a. 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.

  Further, a discontinuous familiar film 85 whose familiarity is discontinuous with the base material as shown in FIG. As an example of such a film, when the base material is an aluminum alloy, there is a film formed by adding a material different from the base material, such as nickel phosphorus plating, to the surface. This makes it possible to select an optimal familiar film regardless of the base material with almost no restriction, so that a highly familiar film can be provided on the swivel piston 3. Therefore, even if the shape accuracy of the swivel piston 3 is relaxed, high performance can be realized, and there is an effect of cost reduction.

  Next, the rolling cylinder 1 will be described with reference to FIG. The rolling cylinder 1 basically has a configuration in which a rolling cylinder 1b and a rolling end plate 1a having a diameter larger than that of the rolling cylinder 1b are combined. Therefore, the rolling end plate 1a is in a state of protruding uniformly from the lower surface portion of the rolling cylinder 1b. A cylinder groove 1c is provided on the upper surface side of the rolling cylinder 1b. The cylinder groove 1c has a cylinder axis perpendicular to the rolling cylinder axis as the central axis of the rolling cylinder 1 as the central axis.

  The cylinder groove 1c has flat side surfaces parallel to each other, and the bottom surface is parallel to the upper surfaces of the cylinder column 1b and the rolling end plate 1a. The cylinder groove 1c extends to the outer periphery of the rolling cylinder 1b. 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. Then, the piston cut surface 3 c is fitted into the side surface of the cylinder groove 1 c so that the rolling cylinder 1 is engaged with the revolving piston 3. Here, since the turning piston 3 is turned by the crankshaft 6, an eccentric shaft insertion hole 1d is provided at the center of the bottom surface of the cylinder groove 1c. Further, an additional familiar film 85 as shown in FIG. 14 may be provided on the entire surface of the rolling cylinder 1 in the same manner as the swing piston 3. Thereby, there exists an effect similar to the case where the additional familiar film 85 is provided in the turning piston 3.

  Next, the stationary cylinder 2 will be described with reference to FIGS.

  The stationary cylinder 2 is basically cylindrical, and a circular cylinder hole 2b (eccentric cylinder hole) is formed in the cylinder mounting surface 2a on the lower surface. Further, the simplest fixing pin 5 is fixedly arranged in the cylinder hole 2b at a position 2E away from the center of the cylinder hole 2b. The fixing pin 5 has a small hole formed in the bottom of the cylinder hole 2b and press-fitted there. Other arrangement methods for the fixing pin 5 include adhesion, welding, and screwing. Further, a suction hole 2s1 connected to the cylinder hole 2b from the upper surface and a suction groove 2s2 on the upper surface of the cylinder hole 2b connected to the cylinder hole 2s are provided. These suction holes 2s1 and suction grooves 2s2 constitute a suction flow path 2s. Further, the cylinder outer discharge groove 2d3 in the vertical direction is provided on the outer peripheral side surface, the cylinder inner discharge groove 2d1 is provided on the cylindrical peripheral surface of the cylinder hole 2b, and the cylinder discharge hole 2d2 connecting the two discharge grooves is provided, thereby forming the discharge flow path 2d. .

  Further, two bypass holes 2e penetrating from the upper surface of the stationary cylinder 2 to the cylinder hole 2b are provided near the side surface of the cylinder hole 2b. A bypass valve 22 is provided on the upper surface side of the stationary cylinders 2. As shown in FIG. 1, the bypass valve 22 is configured such that a valve plate is inserted into a valve seat and the valve plate is lightly pressed from above by a spring. As a result, the bypass valve 22 becomes a one-way valve that allows only the flow in the direction from the cylinder hole 2b to the upper part.

  Further, a back pressure direct current path 200 is provided (the back pressure valve flow path indicated by reference numeral 210 is the third embodiment and is ignored here). As will be described in detail later, the back pressure DC path 200 is formed by connecting a compression chamber side back pressure vertical hole 2h1, a back pressure horizontal hole 2h2, and a back pressure chamber side back pressure vertical hole 2h3. The flow path connects the compression chamber 100 and the back pressure chamber 110 provided on the back side of the revolving piston 3 and the rolling cylinder 1. This includes the role of introducing intermediate pressure from the compression chamber 100 to the back pressure chamber 110, the role of oil flowing into the back pressure chamber 110 flowing out to the compression chamber 100, and promoting oil circulation in the compression section, and the compression chamber 100. It also serves to improve the sealing performance in the compression chamber 100 by refueling.

  Finally, the crankshaft 6 will be described with reference to FIG.

  A shaft collar portion 6d having a large diameter portion is provided at the upper portion of the shaft, and an eccentric portion including an eccentric shaft 6a having an eccentric amount E and a shaft neck 6c having a smaller diameter than the eccentric shaft 6a is provided above the shaft collar portion 6d. And the oil supply vertical hole 6b penetrated to an axial direction through the whole region also including the eccentric part of an upper part from the lower end part of the crankshaft 6 is provided. An oil supply piece 6x is press-fitted into the lower end portion of the oil supply vertical hole 6b, and an oil supply upper main horizontal hole 6e, an oil supply lower main horizontal hole 6f, and an oil supply sub horizontal hole 6g are provided in the horizontal direction. These oil supply lateral holes are installed at positions facing the bearings when the crankshaft 6 is incorporated in an RC compressor. Further, the eccentric shaft 6a is inserted into the swing bearing 23 of the swing piston 3 when the crankshaft 6 is incorporated in the RC compressor. Further, the shaft balance 81 is press-fitted into the shaft collar portion 6d in the direction opposite to the eccentric shaft 6a.

  Next, the assembly of the compression unit components described so far will be described with reference to FIGS. First, the assembly method will be described with reference to FIG.

  As described above, the crankshaft 6 rotatably supported by the main bearing 24 of the frame 4 is positioned in the axial direction by placing the shaft collar portion 6d on the shaft thrust surface 4c. Then, the eccentric shaft 6a is inserted into the eccentric shaft insertion hole 1d of the rolling cylinder 1 so that the eccentric shaft 1a protrudes into the cylinder groove 1c, and then the swing piston 3 is inserted so that the eccentric shaft 6a is inserted into the swing bearing 23. Install into the crankshaft 6. Thereby, the orbiting piston 3 can rotate around the central axis of the eccentric shaft 1a. That is, the central axis of the eccentric shaft 1 a coincides with the piston rotation axis 88 that is the rotation axis of the orbiting piston 3.

  A shaft neck 6c having a smaller diameter than the eccentric shaft 6a is provided between the eccentric shaft 6a and the shaft collar portion 6d so as to pass through the eccentric shaft insertion hole 1d. Further, the orbiting piston 3 is assembled into the rolling cylinder 1 in a state in which the piston cut surface 3c is fitted into the side surface of the cylinder groove 1c so as to be slidable in the cylinder groove 1c. As a result, the cylinder groove 1 c is partitioned into two working chambers by the orbiting piston 3.

  The stationary cylinder 2 incorporating the pin mechanism (the stationary cylinder 2 having the fixed pin 5) combines the assembly of the crankshaft 6, the rolling cylinder 1 and the rotating piston 3 formed as described above by the method described below. After that, the cylinder bolt 90 (see FIG. 1) in a state where the intermediate line 63 between the pin shaft 61 and the central shaft 62 of the cylinder hole 2b (which coincides with a rolling cylinder shaft 89 described later) coincides with the shaft shaft 87. ) To attach to the frame 4.

  First, the fixed pin 5 is inserted into the slide groove 3b of the orbiting piston 3, and the slide shaft that is the central axis of the slide groove 3b and the pin shaft 61 are orthogonal to each other to constitute a pin slide mechanism. Further, the rolling cylinder 1b of the rolling cylinder 1 is mounted in the cylinder hole 2b, and the center line of the cylinder hole 2b is aligned with the rolling cylinder shaft 89. As a result of the above combination, the distance between the shaft shaft 87 and the pin shaft 61 and the distance between the shaft shaft 87 and the rolling cylinder shaft 89 are both E, and the pin shaft 61 is centered on the shaft shaft 87. The rolling cylinder shaft 89 is disposed at a point-symmetrical position. The piston rotation shaft 88 is circularly moved with the turning radius E passing through the pin shaft 61 and the rolling cylinder shaft 89 around the shaft shaft 87 by rotation of the crankshaft 6 (this time, clockwise when viewed from above the compressor). I do.

  Incidentally, as will be described later, the revolving piston 3 reciprocates in the cylinder groove 1c. For this reason, it is necessary to extend the length of the turning piston 3 so that the eccentric shaft insertion hole 1d is hidden by the turning piston 3 even when the turning piston 3 approaches the end of the cylinder groove 1c. When the length of the swiveling piston 3 increases, it is necessary to increase the length of the cylinder groove 1c, and the diameter of the rolling cylinder 1 increases. When the diameter of the rolling cylinder 1 increases, the diameter of the stationary cylinder 2 into which the rolling cylinder 1 is incorporated increases, so that the diameter of the chamber 8 increases and the RC compressor becomes larger. As shown in FIG. 1, the shaft neck 6c is provided so that the eccentric shaft insertion hole 1d passes through the shaft neck 6c having a smaller diameter than the eccentric shaft 6a. As a result, since the eccentric shaft insertion hole 1d can be made small, an increase in the diameter of the RC compressor can be suppressed.

  The configuration of the compression section of the RC compressor incorporating the compression element as described above will be described with reference to the cross sections of FIGS.

  In the middle of the compression operation, two working chambers are formed adjacent to the two piston cylindrical circumferential surfaces 3e of the orbiting piston 3, but in both of FIGS. This is a state where the working chamber has the maximum volume. That is, the working chamber having a volume of 0 is the discharge chamber 105 in which the discharge stroke is completed or the suction chamber 95 that starts the suction stroke, and the working chamber having the maximum volume is the suction chamber 95 or the compression stroke in which the suction stroke is completed. It is the compression chamber 100 which starts. As will be described later, the rotation direction of the crankshaft 6 and the rotation direction of the rolling cylinder 1 are the same. In the drawing, since the crankshaft 6 rotates clockwise, the rolling cylinder 1 also rotates clockwise (indicated by arrows indicating the rotation direction of the rolling cylinder 1 in FIGS. 2 and 3). Therefore, when the rolling cylinder 1 rotates in the clockwise direction, the suction chamber 2s is provided in order to start the suction stroke of the zero-volume working chamber (the left working chamber of the swiveling piston 3) in FIGS.

  Specifically, as shown in FIGS. 2 and 3, the position of the suction hole 2s1 in the stationary cylinder 2 is determined so that the side surface of the suction hole 2s1 starts to communicate with the working chamber. Further, when the rolling cylinder 1 is slightly rotated counterclockwise (when the time of FIGS. 2 and 3 is slightly traced back), the working chamber whose volume is maximum in FIGS. 2 and 3 is in the suction stroke. Is provided with a suction flow path 2s. Specifically, as shown in FIGS. 2 and 3, the suction groove 2 s 2 at the bottom of the cylinder hole 2 b connected to the suction hole 2 s 1 is to continue to communicate with the working chamber (the right working chamber of the swiveling piston 3) that is the suction chamber 95. It is the structure which extended | stretched (refer the dashed-two dotted line of FIG. 3). Although the suction hole 2s1 is provided in the vertical direction this time, it is not limited thereto, and may be provided in the horizontal direction. In this case, since the suction hole 2s1 and the chamber 8 are close to each other, the suction pipe 50 in the RC compressor can be shortened, and suction overheating can be suppressed and performance can be improved.

  Further, when the rolling cylinder 1 rotates clockwise, a sealed state is started in which the working chamber having the maximum volume in FIGS. 2 and 3 does not allow the discharge passage 2d and the suction passage 2s to communicate with each other so as to continue the compression stroke. The sealed state continues until the compression chamber 100 is reduced to the volume of the inherent volume ratio (volume of the suction chamber 95 at the completion of the suction stroke / volume of the compression chamber 100 at the start of the discharge stroke) and starts the discharge stroke. 2 and 3 show the case where the specific volume ratio is 2.2. That is, when the volume of the compression chamber 100 is reduced to the volume of the suction chamber 95 at the completion of the suction stroke divided by 2.2, the cylinder internal discharge groove 2d1 that forms the discharge flow path 2d together with the cylinder through discharge hole 2d2 and the cylinder external discharge groove 2d3. Is provided at a position where communication with the compression chamber 100 starts. From that time, the compression chamber 100 becomes the discharge chamber 105, and the cylinder internal discharge groove 2d1 is provided so as to communicate with the discharge chamber 105 during the entire discharge stroke. In addition, although the case where the specific volume ratio is 2.2 is shown here, the specific volume ratio is not limited to this value, and it is only necessary to obtain compression and discharge functions as a compressor.

  Finally, when the discharge stroke in which the volume of the discharge chamber 105 becomes zero (see the working chamber with the volume 0 in FIGS. 2 and 3), the cylinder internal discharge groove 2 d 1 is positioned and sized so as to be disengaged from the discharge chamber 105. Provided. In this example, the discharge portion directly communicating with the discharge chamber 105 is the cylinder internal discharge groove 2d1 provided on the cylindrical peripheral surface of the cylinder hole 2b. However, the present invention is not limited to this, and a groove provided on the bottom of the cylinder hole 2b such as the suction groove 2s2. It is good. In this case, the discharge flow path 2d can be set even when the specific volume ratio is large and the compression chamber 100 must be compressed until the volume of the compression chamber 100 at the start of the discharge stroke is reduced.

  The description of the configuration of the compression unit is thus completed. Next, the operation of the compression unit will be described with reference to FIGS. 9, 10 and 11 (both cross sections slightly lower than the BB cross section of FIG. 1). Here, since the suction groove 2s2 is in front of the BB cross section of FIG. 1, it must be represented by a two-dot chain line as an imaginary line. However, since the two-dot chain line in the small figure is difficult to distinguish from the solid line, this time, it is indicated by a broken line for convenience.

  First, the flow of the working fluid including the compression operation will be described. The compression operation of the RC compressor using the pin slide mechanism as the rotation half mechanism is described in detail in Patent Document 1, which can be regarded as the same except that the time difference between the end of the suction stroke and the start of the discharge stroke is set to be extremely small. Therefore, only a brief description will be given here. Moreover, the overcompression suppressing means not described in Patent Document 1 will also be described.

  FIG. 9 shows the state of the compression element every 45 degrees while the crankshaft 6 makes one clockwise rotation around the shaft axis 87 (intersection of the center lines in each figure). The entire stroke of the compression operation (suction stroke, compression stroke, discharge stroke) is completed by rotating the crankshaft 6 twice. For this reason, FIG. 9 shows only half of the stroke, but in parallel, the fact that the two working chambers change by one rotation at the crank angle is used to change the stroke of the second rotation to that of the other working chamber. Explain using change. The description will be made of the stroke of the working chamber on the left side of the swiveling piston 3 in the upper left diagram of FIG. The crank angle at this time is set to 0 degree.

  In the upper left diagram of FIG. 9 (see FIG. 10 which is an enlarged view) of FIG. 9 in which the crank angle is 0 degree, the piston rotation shaft 88 overlaps the pin shaft 61. And the volume becomes zero. This is a transition time when the previous discharge stroke ends and the suction stroke starts. If the volume can be strictly reduced to 0, even if both the flow paths and the working chamber communicate with each other, it does not matter. However, when the piston cylindrical peripheral surface 3e collides with the inner peripheral surface of the cylinder hole 2b, the reliability is impaired, and problems such as an increase in noise and vibration, and a decrease in efficiency due to an increase in sliding loss at the collision location arise.

  For this reason, at the worst, it is necessary to set a tolerance so that the piston cylindrical circumferential surface 3e does not collide with the inner circumferential surface of the cylinder hole 2b. Therefore, a small volume actually remains. That is, a gap larger than the other part (between the outer peripheral surface of the rolling cylinder 1b and the inner peripheral surface of the cylinder hole 2b) is formed between the piston cylindrical peripheral surface 3e and the inner peripheral surface of the cylinder hole 2b. For this reason, if both flow paths are connected to this working chamber, the clearance between the piston cylindrical peripheral surface 3e and the inner peripheral surface of the cylinder hole 2b becomes an internal leakage flow path, and the working fluid to be discharged returns to the suction side. Reduces efficiency.

  Therefore, in an actual setting, the flow paths 2s and 2d are not communicated. However, the period during which the two flow paths 2s and 2d are not communicated with the working chamber is extremely short, and is not clearly shown in FIGS.

  Thereafter, when the crankshaft 6 is slightly rotated clockwise, the working chamber communicates with the suction passage 2 s and the working fluid flows from the suction pipe 50 to become the suction chamber 95. Thereafter, as the crank angle increases, the turning piston 3 turns by the same amount as the increase of the crank angle. On the other hand, as is apparent from FIG. 9, the cylinder groove 1c into which the revolving piston 3 is fitted with a clearance rotates with a rotation amount that is half of the revolving amount. By this turning of the turning piston 3 and the rotation of the cylinder groove 1c, that is, the rotation of the rolling cylinder 1, the turning piston 3 moves in the cylinder groove 1c toward the other end. That is, the volume of the suction chamber 95 continues to increase and the suction stroke continues. This movement continues until the crank angle is 360 degrees, that is, until the crankshaft 6 completes one rotation. During this time, the piston rotation shaft 88 draws a turning locus circle 96 shown in FIG.

  Here, when the crank angle is 180 degrees, the piston rotation shaft 88 and the rolling cylinder shaft 89 coincide. For this reason, the rolling cylinder 1 is engaged even if it causes an irregular rotation different from the regular rotation that rotates with half the amount of revolution of the orbiting piston 3.

  In an actual case, the above-mentioned irregular rotation of the rolling cylinder 1 frequently occurs due to a deviation from the ideal rotation that comes from the clearance between the rolling cylinder 1, the revolving piston 3, and the stationary cylinder 2. Once this irregular rotation occurs, as pointed out in Patent Document 1, it is impossible to mechanically automatically return to the regular rotation, and the compression operation stops. In this embodiment, in order to avoid such a locked state at all times and continue a smooth compression operation, in this embodiment, a rotation synchronization means for synchronizing the rotation of the rolling cylinder 1 and the rotation of the swing piston 3 is provided. A rotation half means for reducing the rotation amount of the piston 3 to half of the turning amount is provided.

  First, the rotation of the rolling cylinder 1 is always defined by the rotation of the orbiting piston 3 by the rotation synchronization means. This is achieved by fitting the piston cut surface 3c of the orbiting piston 3 to the side surface of the cylinder groove 1c. Then, by combining the rotation half means, the rotation amount of the rolling cylinder 1 synchronized with the rotation of the swing piston 3 can be defined as half the swing amount of the swing piston 3. In other words, the rotation of the rolling cylinder 1 can always be regulated to normal rotation.

  As described in Patent Document 1, the rotation halving means of the orbiting piston 3 is inserted into the slide groove 3b provided on the piston upper surface 3d, which is the upper surface of the orbiting piston 3, and the fixing pin 5 fixedly arranged on the stationary cylinder 2 is inserted. This is realized by a pin slide mechanism configured by The degree of regulation (the degree of regulation) that regulates the amount of rotation of the orbiting piston 3 by the pin slide mechanism to half of the amount of revolution varies with the crank angle. As described in Patent Document 1, while the crank angle is maximum at 180 degrees, when the crank angle is 0 degrees (see FIG. 11 of Patent Document 1), the pin shaft 61 and the piston rotation shaft 88 coincide with each other. Since the amount of rotation of the orbiting piston 3 is not defined by the pin slide mechanism, it can be seen that the degree of specification is minimized. However, when the crank angle is 0 degree, the piston rotation shaft 88 and the rolling cylinder shaft 89 are farthest apart from each other, so there is no problem in the compression operation from the beginning, and the pin slide mechanism is unnecessary.

  From the above, the normality of the pin slide mechanism shows an ideal change in which the crank angle where the necessity increases increases near 180 degrees and decreases near the crank angle 0 degrees where the necessity decreases. As a result, there is no need to increase the dimensional tolerance and assembly accuracy of the compression elements constituting the compression mechanism, and the manufacturing cost can be reduced.

  This also shows that the pin slide mechanism increases the frequency of defining the movement of the compression element when the crank angle is around 180 degrees. In other words, the crank angle is concentrated around 180 degrees, and a load is applied to the fixed pin 5 and the slide groove 3b, which are pin mechanisms, and the magnitude of the load is ideal for a compression element that is difficult to predict that arises from the gap between the parts. Due to deviation from movement, it is accompanied by irregular and shocking changes.

  As described above, the pin slide mechanism is subjected to an irregular and shocking load, and therefore it is essential to perform reliable lubrication. By the way, since the load applied to the slide groove 3b acts from the fixed pin 5, the lubrication to the pin slide mechanism may be lubricated to the pin mechanism. Therefore, in the RC compressor that realizes a smooth compression operation by the rotation half means by the rotation synchronization means and the pin slide mechanism, oil supply to the pin mechanism is essential. The description regarding this pin oil supply mechanism will be given in the description of the oil flow described later.

  By the way, the method in which the piston cut surface 3c of the swiveling piston 3 serving as the rotation synchronization means is fitted into the side surface of the cylinder groove 1c is also partitioned by the swiveling piston 3 and functions as a seal portion between the working chambers having a pressure difference. doing. For this reason, there is an effect that the sealing performance is remarkably improved and the compressor efficiency is improved as compared with the line seal as in Patent Document 2.

  The stroke after the second rotation will be described in the other working chamber of FIG. 9 (the right working chamber in the upper right view) as described above. The working chamber which has been the suction chamber 95 so far becomes a sealed space with the suction flow path 2s removed. As a result, a compression stroke is started, and the working fluid in the working chamber is compressed with a reduced volume. That is, the working chamber becomes the compression chamber 100. This compression stroke is completed when the compression chamber 100 communicates with the discharge flow path 2d before reaching the lower left diagram of FIG. 9 where the volume of the compression chamber 100 approaches zero, and the discharge stroke is started and the pressure is increased to increase the discharge pressure. The resulting working fluid is discharged into the RC compressor through the discharge flow path 2d.

  For example, when the volume of the compression chamber at the time of discharge is 1/2 of the volume of the suction chamber 95 at the time of completion of the suction stroke, that is, when the specific volume ratio is 2.2, the compression stroke is completed and the discharge stroke is opened. The timing is shown enlarged in FIG. This discharge stroke continues until the crank angle in FIG. 9 is 360 degrees, that is, the crank angle is 0 degrees. Further, the bypass hole 2e always faces the compression chamber 100 during the compression stroke. Thereby, at the time of overcompression, the bypass hole 2e and the bypass valve 22 of the one-way valve provided in the upper part perform the operation | movement which flows the working fluid in the compression chamber 100 to the in-machine space of the chamber 8 which is discharge pressure. That is, it constitutes an overcompression suppressing means. As a result, excessive compression can be avoided during the overcompression operation, and the compressor efficiency is improved.

  By the way, the bypass hole 2e is disposed at a position facing the discharge chamber 105 for a while after the compression chamber 100 has moved to the discharge chamber 105. This can be seen from the view of the crank angle 225 degrees, which is the discharge stroke in FIG. 9, that the bypass hole 2 e faces the discharge chamber 105. Thus, the bypass hole 2e at this point plays the role of the discharge flow path. Therefore, since the discharge flow path resistance can be reduced, there is an effect that the compressor efficiency is improved.

  Further, it can be seen that the bypass hole 2e faces the suction chamber 95 even when the working chamber is the suction chamber 95. This is apparent from the fact that the bypass hole 2e is fully opened in the right working chamber where the compression stroke is started immediately after the suction stroke is completed in the graph of FIG. As a result, even if liquid compression occurs due to suction of a working fluid containing a large amount of liquefied working fluid or oil, the fluid causing the liquid compression can be discharged from the compression chamber 100 through the bypass hole 2e. It is possible to avoid damage to the compressed part due to the above and improve the reliability.

  In this embodiment, a flapper type valve is used as the bypass valve. Thereby, since the distance from the compression chamber 100 to the valve plate of the bypass valve 22 can be set short, there is an effect that re-expansion loss can be suppressed. Of course, the bypass valve may be a reed valve type. In this case, since the structure is simple, there is an effect of cost reduction.

  Next, the flow of oil in the compression part will be described with reference to FIGS. 9 and 12 (enlarged view of M part in FIG. 3 in the BB cross section in FIG. 1) and FIG. Here, the oil supply to the slewing bearing 23 and the main bearing 24, the oil supply path to the pin mechanism, which is a feature of the present invention, and the differential pressure oil supply for flowing oil through these oil supply paths will be described. And the back pressure support means which avoids the bad effect of the gap expansion by oil supply to a pin mechanism using the back pressure used by differential pressure oil supply is demonstrated. Further, the oil supply to the compression chamber by the back pressure channel for setting the back pressure will be described.

  As described above, the oil supply pipe 6x, the oil supply vertical hole 6b, the oil supply lower main horizontal hole 6f, and the oil supply upper main horizontal hole 6e that are always immersed in the oil storage part 125 provide an oil supply path that connects the oil storage part 125 to the main bearing 24. Further, the oil supply vertical hole 6b is also a hole through which the eccentric shaft 6a at the upper end of the crankshaft 6 passes, so that an oil supply path connected to the swing bearing 23 press-fitted into the swing piston 3 and the slide of the swing piston 3 are provided. An oil supply path that leads to the fixed pin 5 that is a pin mechanism through the groove 3b is formed.

  As described above, since the pressure in the oil storage part 125 is the discharge pressure, the oil in the oil storage part 125 also becomes the discharge pressure. The inner diameters of the oil supply pipe 6x and the oil supply vertical hole 6b are both large, and the slide groove 3b has an opening sectional area larger than that (see FIG. 12). Furthermore, since the fixing pin 5 is provided almost immediately above the oil supply vertical hole 6b (see FIG. 12), the flow path from the oil storage portion 125 to the fixing pin 5 is linear. Therefore, the flow resistance of the pin oil supply passage that is the oil supply passage leading to the fixed pin 5 is extremely small, and it becomes possible to supply oil at the discharge pressure to the fixed pin 5. Adjacent to the fixing pin 5 are a discharge chamber 105 serving as a discharge pressure and a high-pressure compression chamber 100 close thereto.

  However, since the space between these regions and the fixing pin 5 (the clearance between the piston upper surface 3d and the bottom surface of the cylinder hole 2b) is set to a narrow clearance, fluid such as working fluid cannot flow into the fixing pin 5 from these clearances. . Thereby, there is a high possibility that the fixed pin 5 is supplied with oil by the pin oil supply passage having substantially zero flow resistance to the fixed pin 5. Here, the gap between the piston upper surface 3d and the bottom surface of the cylinder hole 2b depends on the bottom surface height of the cylinder groove 1c in which the orbiting piston 3 is installed. That is, it depends on the assembly height of the rolling cylinder 1.

  As can be seen from FIG. 13, the lower surface of the rolling cylinder 1 faces the bed surface 4 d of the frame 4. Therefore, the height of the bed surface 4d defines the gap between the piston upper surface 3d and the bottom surface of the cylinder hole 2b. In this example, the height of the bed surface 4d is set so that the gap between the piston upper surface 3d and the bottom surface of the cylinder hole 2b is about 50 μm at the maximum. Thereby, even if the working fluid tries to flow from the high pressure region to the fixed pin 5 side, it cannot flow due to the large flow path resistance, and pin oiling is not hindered.

  By the way, in order to flow oil through the oil supply passage, means for applying a driving force to the oil is required. In this example, the discharge pressure or lower is placed in a space (hereinafter referred to as a back pressure chamber 110) formed between the lower end of the swing bearing 23 and the upper end of the main bearing 24, that is, below the swing piston 3 and the rolling cylinder 1. (Hereinafter referred to as back pressure. Naturally, the pressure is higher than the suction pressure). This is because the space is an upstream space of each oil supply passage, and the differential pressure oil supply is realized by making the pressure lower than the oil storage portion 125 of the discharge pressure which is the downstream space. Thereby, oil is supplied to the slewing bearing 23 together with the main bearing 24, and there is an effect of improving the reliability of both bearings.

  Furthermore, the oil is also sufficiently supplied to the upper part of the eccentric shaft 6 a in the middle of the oil supply path to the slewing bearing 23. Therefore, the flow resistance of the pin oil supply path to the fixed pin 5 at the upper part of the eccentric shaft 6a is substantially 0 as described above, and thus the discharge pressure oil is supplied to the fixed pin 5 in abundant manner. Thereby, the reliable lubrication to the pin mechanism which is the subject of a pin slide mechanism can be implement | achieved, and there exists an effect of improving the reliability of RC compressor.

  By the way, since oil also flows into the slide groove 3b by the pin oil supply passage, the slide groove 3b is normally filled with oil. From the perspective of FIG. 9, since the fixing pin 5 can be regarded as reciprocating in the slide groove 3b, it is necessary to relax the sealing property and avoid oil compression. Therefore, in this example, as shown in FIG. 13, the upper space of the eccentric shaft 6a is enlarged to prevent oil compression.

  By the way, the direction of relative movement of the fixed pin 5 in the slide groove 3b is always directed to the side where the discharge flow path 2d where the suction flow path 2s is not set is set (moves downward in each figure of FIG. 9). . In view of this, a configuration in which the upper space of the eccentric shaft 6a is narrowed in order to deliberately generate oil compression in the slide groove 3b is conceivable. In this case, the oil pressure becomes a pressure that is slightly higher than the discharge pressure and equal to or higher than the discharge pressure, and oil can be supplied to the discharge pressure area near the discharge flow path 2d, so that leakage of working fluid from the discharge pressure area can be suppressed. It becomes. Thereby, there exists an effect that compressor efficiency improves.

  This is the end of the explanation of the oil supply to each part by the differential pressure oil supply. Next, the adverse effects caused by the installation of the pin oil supply passage and the countermeasures will be described.

  Since the oil supply pressure can be sufficiently poured into the pin mechanism by the pin oil supply passage, the reliability of the fixed pin 5 is improved. As a result, the vicinity of the piston upper surface 3d of the swiveling piston 3 is the discharge pressure. Become. Furthermore, the discharge pressure region also spreads on the upper surface of the rolling cylinder 1b, which is the upper surface of the rolling cylinder 1 adjacent to the piston upper surface 3d. Thereby, the turning piston 3 and the rolling cylinder 1 try to move downward. When this movement occurs, a gap (hereinafter referred to as “upper gap”) between the piston upper surface 3d and the rolling cylinder 1b upper surface and the cylinder hole 2b bottom surface is enlarged. In this case, the working fluid leaks from the discharge chamber 105 and the high-pressure compression chamber 100 close to the discharge pressure to the low-pressure portions through the upper gap. Leakage also occurs in the suction chamber 95, which is a low-pressure space, resulting in internal leakage and reducing the compressor efficiency.

  Further, since the working fluid flows into the pin mechanism described above, the lubrication of the pin becomes uncertain, and in the worst case, the lubrication cannot be performed. If it becomes so, oil supply to the turning bearing 23 will also become uncertain, and the reliability of the fixed pin 5 which is a pin mechanism and the turning bearing 23 will be impaired. From the above, it is essential to take measures to prevent the upper gap from being enlarged even if oil is supplied to the pin mechanism.

  In this example, the back pressure, which is the pressure of the back pressure chamber 110, is increased while adjusting the gaps of the respective parts so that the required amount of oil can be secured by the amount of oil supplied by the differential pressure, and the rolling cylinder 1 and the swing piston 3 are moved by the back pressure. Back pressure support means for constantly energizing the stationary cylinder is used (a method for setting this back pressure will be described later). As a result, the enlargement of the upper gap can be avoided, so that the fixed pin 5, the slewing bearing 23, and the main bearing 24, which are pin mechanisms, can be reliably refueled, and the reliability of the RC compressor can be improved, and Since the internal leakage using the leakage flow path can be suppressed, the compressor efficiency of the RC compressor can be improved.

  A method for setting the back pressure will be described below. This is realized by introducing the pressure of the compression chamber 100 through the back pressure DC path 200 connecting the compression chamber 100 and the back pressure chamber 110 having a pressure close to the back pressure set value.

  The back pressure DC path 200 is provided with a compression chamber side back pressure vertical hole 2h1 at the bottom of the cylinder hole 2b and a cylinder mounting surface 2a with a back pressure chamber side back pressure vertical hole 2h3, which are connected by a back pressure horizontal hole 2h2. It is produced by forming a letter-shaped channel. Here, since the back pressure side hole 2h2 is opened from the outer peripheral side of the stationary cylinder 2, it is sealed with a stopper 92 after processing. The back pressure chamber side back pressure vertical hole 2h3 communicates with the bed outer peripheral groove 4f and is further connected to the back pressure chamber 110 via the bed radiation groove 4e.

  As is clear from FIG. 9, the compression chamber 100 of the RC compressor moves relative to the stationary cylinder 2 by the rotation of the rolling cylinder 1 and the movement of the swiveling piston 3 toward the outer peripheral side. Therefore, by providing a back pressure inlet for the back pressure DC path 200 in the stationary cylinder 2, a desired pressure can be introduced into the back pressure chamber 110. Actually, the back pressure DC path 200 is connected to the compression chamber 100 in such a range that the volume ratio (maximum volume of the suction chamber / compression chamber volume) is a specific volume ratio in which a desired back pressure value is obtained. Provide a back pressure inlet.

  Due to such setting of the back pressure DC path 200, the back pressure becomes higher than the pressure in the compression chamber 100 immediately after the back pressure DC path 200 starts to conduct with the compression chamber 100. As a result, oil flowing into the back pressure chamber 100 can be discharged to the compression chamber side. Thereby, the oil supply to each part can be continued, the reliability of each part that supplies oil and the sealing performance by the oil supply can be continuously ensured, and there is an effect that the operation of the stable compressor is enabled.

  In this example, the back pressure DC path 200 is set at a position that does not face the suction chamber 95, but in some cases, the back pressure DC path 200 may be at a position facing the suction chamber 95 in the initial communication of the back pressure DC path 200. In this case, since the oil can be supplied to the suction chamber 95 by the back pressure DC path 200, it is possible to improve the compressor efficiency by improving the volume efficiency. However, when the oil temperature is high, the suction heating increases, and conversely, the volumetric efficiency may be reduced. Therefore, it is necessary to adjust the communication section of the back pressure DC path 200 according to the operating conditions.

  As described above, the oil that has flowed into the compression chamber 100 through the back pressure DC path 200 improves the sealing performance of the compression chamber 100. Therefore, there is an effect of suppressing the internal leakage of the compression stroke and improving the compression efficiency. Thus, the oil that has flowed into the compression chamber 100 finally moves to the discharge stroke together with the working fluid, and is discharged into the compressor through the discharge flow path 2d as described above.

  In the present embodiment, a flat plate-shaped rolling end plate 1 a perpendicular to the rolling cylinder shaft 89 is provided as a rolling end at the lower end opposite to the cylinder groove 1 c of the rolling cylinder 1. This is because the end plate front surface, which is the upper surface of the rolling end plate 1a, is urged toward the cylinder mounting surface 2a by the urging of the rolling cylinder 1 toward the stationary cylinder 2 by the back pressure support described above. Thereby, the sealing performance between the back pressure chamber 110 and the suction chamber 95, the compression chamber 100, and the discharge chamber 105 is improved, and the effect of suppressing the internal leakage and improving the compressor efficiency is obtained. However, the sealing performance is not perfect and some leakage occurs. In that case, the oil flowing into the back pressure chamber 110 flows into the suction chamber 95 and the compression chamber 100 whose pressure is lower than the back pressure. As a result, the sealing performance is improved. In addition, the oil that has flowed into the suction chamber 95 improves the sealing efficiency of the suction chamber 95, and thus has an effect of improving the compressor efficiency by improving the volume efficiency.

  Furthermore, in this embodiment, since the discontinuous familiar film 85 is provided on the surface of the orbiting piston 3 or the rolling cylinder 1, the upper gap, the end plate front surface (the upper surface of the rolling end plate 1a) and the cylinder mounting surface are provided. 2a and the gap between the piston lower surface 3f and the bottom surface of the cylinder groove 1c are reduced as a whole with shape correction, leakage loss is reduced, and the mutual shape is smoothed to reduce sliding loss. In addition, the compressor efficiency is improved. Further, it is well known on the opposing surface (for example, between the outer peripheral surface of the rolling cylinder 1b and the inner peripheral surface of the cylinder hole 2b and between the piston cut surface 3c and the side surface of the cylinder groove 1c) that is not urged by the back pressure support. After that, since the gap is reduced as compared with the case where the familiar coating is not provided, the sealing performance is improved and the compressor efficiency is improved.

  Furthermore, in this embodiment, the end plate front surface is provided closer to the back surface of the rolling cylinder 1 than the bottom surface of the cylinder groove 1c. That is, the bottom surface of the cylinder groove 1c is made higher than the front surface of the end plate (the upper surface of the rolling end plate 1a) to make a step (see FIG. 4). Thereby, the gap between the outer peripheral surface of the stepped portion and the inner peripheral surface of the cylinder hole 2b is formed in the cylinder groove 1c between the working chamber (suction chamber 95, compression chamber 100, discharge chamber 105) and the back pressure chamber 110. Since there is a gap between the seals, there is an effect of suppressing the leakage of the gap and improving the compressor efficiency.

  In this case, the rolling cylinder 1 and the annular end plate can be separate parts. Then, the machining of the cylinder groove 1c of the rolling cylinder 1 and the machining of the rolling end plate 1a can each be performed by a lathe, which has the effect of reducing the machining cost. Of course, the rolling cylinder 1 and the rolling end plate 1a may be joined by welding, screwing, or the like.

  Next, the RC compressor according to the second embodiment will be described with reference to FIG. FIG. 15 is an enlarged cross-sectional view near the surface of the rolling cylinder 1 or the revolving piston 3, except that the continuous familiar coating 86 whose conformability continuously decreases from the surface toward the inside is shown in Example 1. Because of this, a description of similar parts is omitted. In addition, it is desirable to form the continuous familiar film 86 over the entire sliding surface.

  An example of such a film is a surface-modified familiar film that is immersed in a treatment agent to modify the surface. This is because, as shown in FIG. 15, the constituents are deposited on the surface of the original base material and react with the treatment agent to form a highly-adapted precipitate layer, and the original base material side is eroded and porous. This can be realized by forming an erosion layer that is slightly more familiar to the base material than the base material but less accustomed to the deposited layer. For example, when the base material is cast iron, there is a film formed by manganese phosphate treatment. As a result, the peeling of the film is less likely to occur than in the case of the discontinuous familiar film 85, and the reliability is improved.

  In addition, since a certain degree of familiarity is generated even at the original surface position of the base material, it becomes easy to manage the base material dimensions on which the familiar film is provided. For example, even if the height of the swiveling piston 3 in the base material is slightly larger than the depth of the cylinder groove 1c in the base material, it can be worn down to the size of the base material or less by the continuous familiar coating 86 of the swiveling piston 3. In other words, the tolerance of the base material dimensions can be set to allow mutual interference, so the distance between the dense surfaces (between the base surfaces of the base material) when familiar is reduced, and the sealing performance is further improved and compressed. There is an effect that the efficiency is improved.

  Next, the RC compressor according to the third embodiment will be described with reference to FIGS. 16 and 17. FIG. 16 is an enlarged cross-sectional view of a portion M in FIG. FIG. 17 is a longitudinal sectional view taken along the line OG of FIG. 16 and shows a cross section of a portion where the back pressure valve flow path is installed. Since it is the same as that of Example 1 or 2 except using the back pressure valve flow path 210 as the back pressure setting method for a back pressure support means, the description regarding the same location is abbreviate | omitted.

  The back pressure valve flow path 210 is a U-shaped flow path as in the back pressure DC path 200 of the first embodiment. However, the compression chamber 100 that is in communication is communicated with the compression chamber 100 on the lower pressure side than the back pressure chamber DC path because there is a pressure increase by the back pressure valve 26 described later. For this reason, the position of the vertical hole on the compression chamber 100 side is changed to a compression chamber side back pressure valve vertical hole 2h4. Further, since the pressure difference is set by a back pressure valve 26 described later, the diameter of each hole is increased.

  Here, in the case of Example 1 or 2 where the slide groove 3b is connected to the piston cut surface 3c, the compression chamber side back pressure valve vertical hole 2h4 is formed in the slide groove 3b between the crank angle 225 degrees and the crank angle 270 degrees in FIG. I will come. Since the slide groove 3b is filled with the discharge pressure oil and the discharge pressure working fluid foamed from the slide groove 3b, there is no discharge pressure in the compression chamber side back pressure valve vertical hole 2h4 or the space of the back pressure valve flow path 210 connected thereto. Fluid flows in. When the compression chamber side back pressure valve vertical hole 2h4 faces the compression chamber 100, the fluid flows into the compression chamber 100 having a pressure lower than the discharge pressure to cause internal leakage. Therefore, in this embodiment, the slide groove both ends sealing portion 3b1 shown by cross-hatching in FIG. 16 is provided to avoid the above-described internal leakage and suppress performance degradation.

  Thereby, since the drill blade used for processing can be changed to a thick one, there is an effect that the risk of damage is reduced, processing is facilitated, and processing cost is reduced. In addition to the U-shaped flow path configured as described above, in this example, the back pressure valve hole 2h5 is processed from the upper surface side of the stationary cylinder 2, and the back pressure valve 26 is installed therein. Therefore, the back pressure valve flow path 210 includes the compression chamber side back pressure valve vertical hole 2h4, the back pressure horizontal hole 2h2, the back pressure chamber side back pressure vertical hole 2h3, the back pressure valve hole 2h5, and the back pressure valve 26. The back pressure chamber side back pressure vertical hole 2h3 communicates with the bed outer peripheral groove 4f, and is further connected to the back pressure chamber 110 via the bed radiation groove 4e.

  Next, a procedure for producing the back pressure valve flow path 210 will be described with reference to FIG.

  First, the back pressure valve piece 26a is press-fitted and fixed to the bottom of the back pressure valve hole 2h5. Then, the back pressure valve plate 26b is placed thereon, the back pressure valve spring 26c is disposed thereon, and the back pressure valve hole 2h5 is sealed with the back pressure valve cap 26d. At this time, the back pressure valve spring 26c is compressed and presses the back pressure valve plate 26b against the back pressure valve piece 26a with a predetermined force.

  As a result, when the back pressure becomes higher by a certain value corresponding to the pressing force of the back pressure valve spring 26c to the back pressure valve piece 26a than the average pressure of the compression chamber 100 with which the back pressure communicates, the back pressure valve 26 opens and the back pressure valve 26 opens. Control the pressure.

  Here, as the fluid for increasing the pressure in the back pressure chamber 110, the oil flowing into the back pressure chamber 110 is used. That is, the back pressure chamber fluid introduction path is all the inflow path of the oil flowing into the back pressure chamber 110. Specifically, the flow path flows from the main bearing 24 and the flow path flows from the swivel bearing 23.

  By setting the back pressure by the back pressure valve channel as described above, the back pressure value becomes a pressure that is higher by a substantially constant value than the pressure of the compression chamber that communicates. This is because, when the over-compression suppressing means using the bypass valve 22 or the like is employed, the pressure is close to a pressure that is close to the minimum pressure required to urge the swing piston 3 and the rolling cylinder 1 toward the stationary cylinder 2. The sliding loss that occurs with the biasing can be reduced. Therefore, there is an effect that the compressor efficiency can be improved.

  Next, an RC compressor according to Embodiment 4 will be described with reference to FIG. 18 is an enlarged vertical sectional view of a P portion in FIG. In this figure, in order to fix the fixing pin 5 which is the simplest pin mechanism, a pin fixing flange 5 a is provided and fixed with a pin fixing screw 91. Since other than this is the same as in the first to third embodiments, a description of the same part is omitted.

  As described above, an impact load is applied to the fixing pin 5. For this reason, in the case of fixing only the cylindrical surface, since the impact load is received in the linear region, there is a risk that the hole gradually expands and the fixing pin 5 falls off.

  In the present embodiment, by providing the pin fixing flange 5a, an impact load can be received on the surface of the pin fixing flange 5a. Further, since the fixing pin 5 can be fixed by the pin fixing screw 91, the fixing pin 5 can be prevented from falling off, and the reliability of the compressor is improved. In FIG. 18, only one pin fixing screw 91 is provided, but a plurality of pin fixing screws 91 may be used.

  Next, an RC compressor according to Embodiment 5 will be described with reference to FIGS. 19 and 20.

  FIG. 19 is an enlarged vertical sectional view of a P portion in FIG. 1, and FIG. 20 is an enlarged perspective view of the slider.

  In these drawings, a slider 5c that can rotate with respect to the pin shaft is provided, thereby providing a pin mechanism. Since other than this is the same as in the first to fourth embodiments, the description regarding the same part is omitted.

  In this embodiment, as shown in FIG. 19, the pin mechanism has a slider 5 c that is rotatable with respect to a pin shaft and is installed on the lower surface of the fixed pin 5 by a slider holding flange 5 b. The slider 5c is an element that fits into the slide groove 3b. As shown in FIG. 20, the slider 5c has a slider center hole 5c2 and a slider cut surface 5c1. The slider cut surface 5c1 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 holding flange 5b into the slider center hole 5c2 with a small play, the pin mechanism is manufactured by press-fitting into the fixed pin 5.

  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 5c1, and further from the slider center hole 5c2 to the shaft of the slider holding flange 5b. Since the former is between planes and the latter is between cylindrical peripheral surfaces, there is no delivery of loads with concentrated loads. For this reason, the concentration of load in the pin mechanism can be suppressed, and the reliability is improved.

  Next, an RC compressor according to Embodiment 6 will be described with reference to FIGS. 21 and 22. FIG. 21 is an enlarged vertical sectional view of a Q portion in FIG. 1, and FIG. 22 is a perspective view showing a modification of the rolling cylinder 1.

  In these drawings, the rolling end plate 1a, which is the collar portion of the rolling cylinder 1 in FIG. 4, is replaced with a cylindrical rolling cylindrical end portion 1h. Since other than this is the same as in the first to fifth embodiments, the description regarding the same part is omitted.

  Since the rolling cylindrical end 1h opens to the outer peripheral side by back pressure, it is biased to the inner peripheral surface of the cylinder hole 2b of the stationary cylinder 2, and the compression chamber 100 and the suction chamber 95 above the back pressure chamber 110 and the rolling end plate 1a. In addition, the sealing performance with the discharge chamber 105 is improved, and the compressor efficiency is improved. Furthermore, since the rolling end plate 1a does not have a larger diameter than the rolling cylinder column 1b, there is an effect that the diameter of the RC compressor can be reduced.

  1: rolling cylinder, 1a: rolling end plate, 1b: rolling cylinder, 1c: cylinder groove, 1d: eccentric shaft insertion hole, 1h: rolling cylinder end, 2: stationary cylinder, 2a: cylinder mounting surface, 2b: cylinder hole 2d: Discharge flow path, 2d1: Cylinder internal discharge groove, 2d2: Cylinder through discharge hole, 2d3: Cylinder external discharge groove, 2e: Bypass hole, 2h1: Compression chamber side back pressure vertical hole, 2h2: Back pressure horizontal hole, 2h3: Back pressure chamber side back pressure vertical hole, 2h4: compression chamber side back pressure valve vertical hole, 2h5: back pressure valve hole, 2s: suction flow path, 2s1: suction hole, 2s2: suction groove, 3: swirling piston, 3a: swivel bearing hole 3b: Slide groove, 3c: Piston cut surface, 4: Frame, 4d: Bed surface, 5: Fixing pin, 5a: Pin fixing flange, 5b: Slider holding flange, 5c: Sly 5c1: Slider cut surface, 6: Crankshaft, 6a: Eccentric shaft, 6b: Lubricating vertical hole, 6c: Shaft neck, 6d: Shaft collar, 7: Motor, 7a: Rotor, 7b: Stator, 8: Chamber, 8a : Chamber cylindrical portion, 8b: chamber upper lid, 8c: chamber lower lid, 22: bypass valve, 23: slewing bearing, 24: main bearing, 25: auxiliary bearing, 26: back pressure valve, 26a: back pressure valve piece, 26b: Back pressure valve plate, 26c: back pressure valve spring, 26d: back pressure valve cap, 35: lower frame, 50: suction pipe, 55: discharge pipe, 85: discontinuous familiar film, 86: continuous familiar film, 90: cylinder bolt 95: suction chamber, 100: compression chamber, 105: discharge chamber, 110: back pressure chamber, 125: oil storage section, 200: back pressure DC path, 210: back pressure valve flow path, 220: Mechikku terminal.

Claims (15)

A crankshaft having an eccentric shaft with the shaft axis as a rotation center;
A frame that pivotally supports the crankshaft;
A rotational drive source for applying rotational drive torque to the crankshaft;
A compression section for sucking, compressing and discharging the working fluid;
An oil storage part,
The compression portion includes a rolling cylinder having a cylinder groove, a turning piston slidably accommodated in the cylinder groove, and a stationary cylinder having an eccentric cylinder hole that rotatably accommodates the rolling cylinder,
The space surrounded by the rolling cylinder, the turning piston, and the stationary cylinder functions as a suction chamber, a compression chamber, and a discharge chamber as the rolling cylinder and the turning piston rotate.
The eccentric shaft has a centerline different from the shaft axis;
The orbiting piston is disposed so as to be capable of rotating about the center line of the eccentric shaft, and revolves according to the rotation of the crankshaft.
The eccentric cylinder hole of the stationary cylinder is provided with a fixing pin having a center line different from the shaft axis,
The swivel piston has a slide groove, and the fixed pin has a configuration slidably fitted in the slide groove,
The midpoint of the line connecting the intersection of the bottom surface of the eccentric cylinder hole and the center line of the fixing pin and the intersection of the bottom surface of the eccentric cylinder hole and the center line of the rolling cylinder is the center of the eccentric cylinder hole. It is arranged so that it coincides with the intersection of the bottom surface and the center line of the shaft axis, and these three center lines are parallel to each other, whereby the rotation of the orbiting piston and the rotation of the rolling cylinder are synchronized. And adjusting the rotational angular velocity of the orbiting piston to half of the rotational angular velocity of the crankshaft,
The oil storage section is configured such that the pressure of the oil storage section is equal to the pressure of the discharge chamber, and an oil communication path that connects the oil storage section and the slide groove is provided, so that the lubricating oil of the oil storage section is supplied to the fixing pin and the Rolling cylinder positive displacement compressor that supplies slide grooves.   2. The rolling cylinder positive displacement compressor according to claim 1, wherein the oil communication passage is configured by an oil supply vertical hole that passes through the crankshaft and the eccentric shaft and communicates with the slide groove. The orbiting piston has two piston cut surfaces that are parallel and flat to each other;
The cylinder groove has two inner side surfaces that are parallel to each other and flat,
3. The rolling cylinder type positive displacement compressor according to claim 1, wherein the two piston cut surfaces are fitted between the two inner side surface portions so as to be slidable. 4. A back pressure chamber is provided between the rolling cylinder and the frame,
The stationary cylinder has a back pressure DC path that communicates the compression chamber and the back pressure chamber, and the pressure in the back pressure chamber is an intermediate pressure between the pressure in the suction chamber and the pressure in the discharge chamber. The rolling cylinder type positive displacement compressor according to any one of claims 1 to 3, configured as described above.   The rolling cylinder positive displacement compressor according to claim 4, wherein a back pressure valve is attached to a flow path connecting the compression chamber and the back pressure chamber.   The rolling cylinder type positive displacement compressor according to any one of claims 1 to 5, wherein the number of the compression units is one.   The rolling cylinder positive displacement compressor according to claim 6, wherein the compression unit, the rotation drive source, and the oil storage unit are arranged in this order and are connected by the crankshaft. The rolling cylinder has an eccentric shaft insertion hole,
The rolling cylinder type positive displacement compressor according to any one of claims 1 to 7, wherein the revolving piston is configured to close the eccentric shaft insertion hole.   The rolling piston positive displacement compressor according to claim 8, wherein a shaft neck having a diameter smaller than that of the eccentric shaft is provided between the eccentric shaft and a rotation shaft of the crankshaft.   The rolling cylinder positive displacement compressor according to any one of claims 1 to 9, wherein a bypass hole having a bypass valve that is a one-way valve is provided at a bottom portion of the eccentric cylinder hole. The rolling cylinder includes a rolling cylinder having the cylinder groove, and a rolling end plate,
The diameter of the said rolling end plate is a rolling cylinder type positive displacement compressor as described in any one of Claims 1-10 larger than the diameter of the said rolling cylinder. The rolling cylinder is a rolling cylinder having the cylinder groove, and has a configuration in which a rolling end plate which is a separate body from the rolling cylinder is overlaid on the rolling cylinder,
The diameter of the said rolling end plate is a rolling cylinder type positive displacement compressor as described in any one of Claims 1-10 larger than the diameter of the said rolling cylinder.   The rolling cylinder type positive displacement compressor according to claim 11 or 12, wherein a step is provided between a bottom portion of the cylinder groove and an end plate front surface on the cylinder groove side of the rolling end plate.   The rolling cylinder type positive displacement compression according to any one of claims 1 to 10, wherein the rolling cylinder includes a rolling cylinder having the cylinder groove and a rolling cylinder end portion having a diameter equal to that of the rolling cylinder. Machine.   The rolling piston type positive displacement compressor according to any one of claims 1 to 14, wherein a conformal coating is provided on at least one surface of the rolling cylinder and the orbiting piston.

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