JP2019135377A - Rolling cylinder type capacity-type compressor - Google Patents

Abstract

To constantly and sufficiently supply a lubricant to a pin slide mechanism in order to improve the reliability of the pin slide mechanism.SOLUTION: In a rolling cylinder type capacity-type compressor, a turning piston 3, a rolling piston 1 and a stationary cylinder 2 constitute a compression part, a suction chamber 95 and a compression chamber 100 being tow spaces partitioned by the turning piston fit into a cylinder groove are formed between the rolling cylinder and the stationary cylinder 2, and a working fluid in the compression chamber reaches discharge pressure by a motion of the turning piston. The fixed piston is fit into the slide groove, and has a pin slide oil supply path for supplying the oil of an oil storage part 125 to the fixed pin and the slide groove. The pressure of the oil supplied to the fixed pin and the slide groove at an outlet of the pin slide oil supply path is set not lower than the discharge pressure.SELECTED DRAWING: Figure 1

Description

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

  Patent Document 1 discloses a means for solving the problem of pump operation locking in a rolling cylinder type positive displacement pump. In the positive displacement pump described in Patent Document 1, the working fluid is liquid oil, the rotation synchronizing means for synchronizing the rotation amount of the swing piston and the rotation amount of the rolling cylinder, and the rotation amount of the swing piston. Is provided with a means for half-rotating the rotation. That is, the rotation half means can be regarded as the attitude control means of the orbiting piston. By these means, half of the turning amount of the turning piston becomes equal to the amount of rotation of the rolling cylinder, and the pump operation is performed.

JP 2010-185358 A

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

  However, when the working fluid is a gas that is less lubricious than oil, the pin slide mechanism cannot be secured by the method of disposing the pin slide mechanism in the discharge flow path, and the pin slide mechanism wears out. Decrease in reliability is a problem. In the vicinity of the pin slide mechanism, there are a suction chamber having the lowest suction pressure, a compression chamber changing to the highest discharge pressure, and a discharge chamber having the discharge pressure. Therefore, in order to constantly and reliably supply the pin slide mechanism, it is necessary to increase the pressure of the oil supplied to the pin slide mechanism until it resists the surrounding pressure.

  In the present invention, when the pin slide mechanism is applied to the rotation half means of the rolling cylinder type positive displacement compressor, the lubricating oil to the pin slide mechanism is always sufficiently supplied in order to improve the reliability of the pin slide mechanism. For the purpose.

  A rolling cylinder type positive displacement compressor according to the present invention includes a swing piston having a slide groove, a rolling cylinder having a cylinder groove, a stationary cylinder having a fixed pin, and a piston swing drive source that is a drive source for the swing motion of the swing piston. And a drive transmission unit that connects the swing piston and the piston rotation drive source, a frame through which the drive transmission unit passes, a rotation piston, a rolling cylinder, a stationary cylinder, a piston rotation drive source, and a drive transmission unit. A revolving piston, a rolling cylinder and a stationary cylinder constitute a compression portion, and two revolving pistons fitted in a cylinder groove partition between the rolling cylinder and the stationary cylinder. A suction chamber and a compression chamber are formed, and the working fluid in the compression chamber The fixed pin is fitted into the slide groove, and has a pin slide oil supply passage for supplying oil from the oil storage section to the fixed pin and the slide groove. The pressure of the oil supplied to the outlet of the pin slide oil supply passage is set to be equal to or higher than the discharge pressure.

  According to the present invention, the lubricating oil can always be reliably supplied to the sliding portion of the compression portion of the rolling cylinder positive displacement compressor, and the wear of the sliding portion can be avoided to improve the reliability of the compressor. be able to.

It is a longitudinal cross-sectional view which crosses the bypass valve and discharge flow path of RC compressor which concerns on Example 1. FIG. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. 1 is a perspective view illustrating a rolling cylinder of an RC compressor according to Embodiment 1. FIG. 1 is a perspective view showing a turning piston of an RC compressor according to Embodiment 1. FIG. It is a bottom view which shows the stationary cylinder which has a fixing pin concerning Example 1. FIG. 1 is a perspective view showing a frame of an RC compressor according to Embodiment 1. FIG. 1 is an exploded perspective view illustrating a configuration of a compression unit of an RC compressor according to Embodiment 1. FIG. FIG. 2 is a flowchart illustrating a compression operation of the RC compressor according to the first embodiment with reference to a cross-sectional view slightly deviated toward the swivel piston side from the BB cross section of FIG. 1. FIG. 10 is an enlarged cross-sectional view showing an 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 RC compressor according to the first embodiment shifts from a compression stroke to a discharge stroke. It is an expanded sectional view of the P section of FIG. It is an expanded sectional view which shows the modification of FIG. It is an expanded sectional view of the M section of FIG. FIG. 13 is an enlarged cross-sectional view illustrating a part M of FIG. 12 in Example 2. It is a perspective view which shows the slider of the pin slide mechanism of RC compressor which concerns on Example 2. FIG. FIG. 13 is an enlarged cross-sectional view illustrating a part M of FIG. 12 in Example 3. FIG. 10 is a perspective view illustrating a slider of a pin slide mechanism of an RC compressor according to a fourth embodiment. FIG. 10 is an enlarged cross-sectional view schematically showing the vicinity of the surface of a rolling cylinder, a revolving piston, or a stationary cylinder of an RC compressor according to a fifth embodiment. FIG. 10 is an enlarged cross-sectional view schematically showing the vicinity of the surface of a rolling cylinder, a revolving piston, or a stationary cylinder of an RC compressor according to a sixth embodiment. FIG. 9 is an enlarged cross-sectional view illustrating a Q portion in FIG. 1 in Example 7. FIG. 10 is a perspective view illustrating a rolling cylinder of an RC compressor according to a seventh embodiment. FIG. 10 is a perspective view showing a rolling cylinder of an RC compressor according to an eighth embodiment. FIG. 10 is a top view illustrating a rolling cylinder of an RC compressor according to an eighth embodiment. FIG. 10 is a perspective view showing a rolling cylinder of an RC compressor according to a ninth embodiment. FIG. 10 is a top view illustrating a rolling cylinder of an RC compressor according to a ninth embodiment. FIG. 10 is a perspective view illustrating a rolling cylinder of an RC compressor according to a tenth embodiment. It is a perspective view from the lower part of the stationary cylinder of the RC compressor concerning Example 11. FIG. 14 is a longitudinal sectional view across a bypass valve and a discharge flow path of a horizontal RC compressor according to Embodiment 12. It is a longitudinal cross-sectional view which crosses the bypass valve and discharge flow path of the lower compression vertical RC compressor by which the compression part which concerns on Example 13 is arrange | positioned below. It is an expanded sectional view which shows the S section of FIG. 30 in Example 13. It is an expanded sectional view which shows the S section of FIG. 30 in the modification of Example 13. It is an expanded sectional view which shows the R section of FIG. 30 in Example 13. It is an expanded sectional view showing the N section of Drawing 31A in Example 13. It is an expanded sectional view showing the N section of Drawing 31A in Example 14. It is an expanded sectional view showing the N section of Drawing 31A in Example 15. It is an expanded sectional view showing the N section of Drawing 31A in Example 16. FIG. 32 is a flowchart showing a pin slide pump operation of the RC compressor according to the embodiment 16 using a view seen from a cross section slightly deviating to the swivel piston side from the BB cross section of FIG. 30. It is an expanded sectional view which shows the S section of FIG. 30 in Example 17. It is an expanded sectional view in the surface orthogonal to FIG. It is an expanded sectional view which shows the E section of FIG. 38 in Example 17. FIG. It is an expanded sectional view which shows the E section of FIG. 38 in Example 18. FIG. It is an expanded sectional view which shows the U section of FIG. It is a schematic diagram of the W section of FIG.

  The present invention is a compressor having a typical configuration in which three main compression elements are a revolving piston that revolves, a rolling cylinder that rotates in conjunction with a stationary cylinder, and a stationary cylinder that incorporates them. The present invention relates to a rolling cylinder positive displacement compressor (hereinafter also referred to as “RC compressor”) that compresses a gas that is a working fluid by a compression element.

  In particular, rotation synchronization means for synchronizing the rotation speeds of the orbiting piston and the rolling cylinder, in order to avoid a mechanism stop that occurs very frequently at the timing when the piston rotation axis and the cylinder rotation axis overlap, and to continue the compression operation smoothly, The present invention relates to a rolling cylinder type positive displacement compressor provided with a swing piston posture restricting means by a rotation half means that regulates the rotation speed of the piston to half of the swing speed.

  The rotation synchronizing means and the rotation half means are realized by a pin slide mechanism using a pin mechanism fixedly arranged or rotatably supported by the slide groove of the swing piston and the stationary cylinder. Thereby, even if it uses one compression part, the positive displacement compressor which can continue compression operation is realizable. For this reason, it is optimal for a compressor having a small displacement volume even if it has a large capacity for use under a high capacity such as a small capacity or carbon dioxide, and there is an effect that the compressor can be miniaturized. Of course, a plurality of compression units may be provided in order to suppress fluctuations in rotational torque. This time, it is an embodiment having one compression section.

  The rolling cylinder positive displacement compressor is a high-pressure chamber system in which the casing is filled with discharge gas. This blows out discharge gas, which is a working fluid containing oil, from the compression section to the casing space, where the oil is separated from the discharge gas. The separated oil returns to the oil storage section provided at the bottom in the casing. As a result, the oil in the oil storage section is almost discharged. More specifically, the surface of the oil storage part becomes the discharge pressure, and the oil below the surface becomes a pressure higher than the discharge pressure by the amount of oil from the surface.

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

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

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

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

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

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

  The rotation synchronizing means synchronizes the piston rotation amount, which is the rotation angle amount of the orbiting piston, with the cylinder rotation amount, which is the rotation angle amount of the rolling cylinder.

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

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

  The casing incorporates an oil storage part together with the compression part.

  The stationary cylinder is provided with a suction channel and a discharge channel.

  Of the two working chambers, the suction flow path connects one working chamber whose volume is increased by the swiveling motion of the swiveling piston to the suction system to serve as a suction chamber.

  In the discharge flow path, the other working chamber whose volume is reduced by the revolving motion of the revolving piston is connected to the discharge system to be a discharge chamber.

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

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

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

  The rolling cylinder type positive displacement compressor according to the present invention includes a pin slide oil supply passage for supplying oil in the oil storage portion to the pin slide mechanism, and pressure in the pin slide mechanism portion for oil flowing through the pin slide oil supply passage. And a pin slide oil pressure increasing means for making the pressure equal to or higher than the discharge pressure.

  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 the drawings, common parts will be described using the same drawings. Moreover, the same code | symbol in the figure of each Example shows the same thing or an equivalent, and the overlapping description is abbreviate | omitted. Note that, in the portions other than those described as schematic illustrations, the dimensional ratios of the respective elements shown in the drawings indicate one embodiment. Therefore, the size relationship and angle of each dimension in the illustrated shape also indicate an embodiment. Here, the specific dimension value is not particularly limited, but it is desirable that the outer diameter of the rolling cylinder type positive displacement compressor is in a range from 10 mm to 2000 mm.

  The RC compressor according to the first embodiment will be described with reference to FIGS. In this RC compressor, a compression part is arranged at the upper part in the casing, and a motor as a piston turning drive source is arranged below the compression part, and a crankshaft (drive transmission part) constituting drive transmission means is connected vertically. It is an upper compression vertical type arranged in a direction (longitudinal direction). Also, here, the pin axis is set at a position rotated 180 degrees from the cylinder rotation axis on the piston turning locus circle passing through the cylinder rotation axis, and the slide axis is the normal direction of the cut axis around the piston rotation axis The description will focus on what is provided in. That is, the pin shaft adjustment angle δ is 0 degree. In addition, the description regarding this pin axis adjustment is described in prior art documents.

  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 and C3 are in two places in FIGS. 2 and 3, respectively, which means that two C2s and two C3s are 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. Further, FIG. 9 is an explanatory view of the compression operation using a cross section slightly shifted to the swivel piston side from the BB cross section 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 when a bypass valve 22 described later does not operate, and shows a state between the crank angle of 180 degrees and 225 degrees in FIG. It is shown. FIG. 12 is a longitudinal sectional view of the pin mechanism attaching portion, an enlarged view of a portion P in FIG. 1, and FIG. 13 is a modification of the first embodiment shown in FIG. Finally, FIG. 14 shows the insertion of the slide groove of the pin slide mechanism, and is an enlarged vertical sectional view of the M part in FIG. 12 or 13.

  First, after describing the overall configuration of the RC compressor, main components and their configuration methods will be described. A method for configuring the compression unit, which requires detailed description, will be described in the latter half. Next, the flow of the working fluid in the RC compressor will be described. Among these, the flow of the compression unit will be described in detail in the latter half along with the operation thereof. Lastly, the flow of oil in the RC compressor will be described.

  Initially, the whole structure of RC compressor is demonstrated using FIG.

  The compression unit includes a swiveling piston 3, a rolling cylinder 1, and a stationary cylinder 2 as components that directly act on the compressed working fluid. Then, regarding these materials, if the revolving piston 3, the rolling cylinder 1 and the stationary cylinder 2 are all made of cast iron, the cost can be kept low.

  Alternatively, the rolling cylinder 1 may be made of an aluminum alloy, and the turning piston 3 and the stationary cylinder 2 may be made of cast iron. If it does in this way, since the rolling cylinder 1 can be reduced in weight, it can become difficult to raise | generate a malfunctioning and can drive | operate smoothly.

  Furthermore, if the revolving piston 3, the rolling cylinder 1 and the stationary cylinder 2 are all made of an aluminum alloy, the entire RC compressor can be reduced in weight.

  The compression part 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. A motor 7 is provided on the crankshaft 6 while the compression portion is fixedly disposed on the casing cylindrical portion 8a by welding or the like. The motor 7 includes a stator 7b fixedly disposed on the casing cylindrical portion 8a and a rotor 7a fixedly disposed on the crankshaft 6. Here, the motor 7 is a piston rotation drive source, and is also a shaft rotation drive source. 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 serve to dynamically balance the unbalance of the compression element (slewing piston 3) that swirls in the compression operation.

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

  In addition, a positive displacement oil pump 200 (oil supply pump) is provided at the lower end of the crankshaft 6. This positive displacement oil pump 200 is an oil pump represented by a trochoidal tooth type or cycloid tooth type gear pump, and has a boosting capability. The crankshaft 6 is provided with an oil supply vertical hole 6b (oil supply passage) 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.

  A casing lower lid 8c is welded to a lower portion of the casing cylindrical portion 8a, and a casing upper lid 8b is welded to an upper portion thereof. A lower cover 8c). Here, oil is sealed at an appropriate stage of assembling the RC compressor, and an oil storage part 125 for storing the oil is formed in the vicinity of the casing lower lid 8c which is the lowermost part.

  A suction pipe 50 for introducing a working fluid from the outside to a compression section provided inside the sealed casing 8 is provided in the casing upper lid 8b. Further, the casing upper lid 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, main components of the RC compressor will be described individually.

  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 collar receiving surface 4c is provided around the upper surface of the main bearing hole 4b, and a collar receiving notch 4c1 serving as an outlet passage for the oil that lubricates the main bearing 24 is provided at one or a plurality of positions. Then, a bed surface 4d on which the rolling cylinder 1 is placed is provided at a position surrounding the collar receiving surface 4c. The bed surface 4d is provided with a bed radiation groove 4 serving as an oil passage. On the other hand, a frame outer peripheral groove 4 m is provided on the outer periphery of the frame 4.

  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. Two piston cut surfaces parallel to each other and parallel to the slewing bearing axis are provided on two side surfaces of the slewing piston 3 with the cut axis being an axis perpendicular to the slewing bearing axis being the central axis of the slewing bearing 23 as the central axis. 3c is provided. Then, two piston cylindrical peripheral surfaces 3e whose centers connecting the two piston cut surfaces 3c are shifted are provided.

  Further, a piston upper surface 3d and a piston lower surface 3f, which are flat surfaces parallel to each other and perpendicular to the slewing bearing shaft, are provided on the upper and lower sides. Then, on the upper surface 3d of the piston, a slide groove 3b having a constant width is provided with the slide axis orthogonal to the slewing bearing axis as the central axis and parallel to the slewing bearing axis. The slide groove 3b is set to a depth communicating with the slewing bearing hole 3a, and the oil supply path to the slewing bearing 23 and the oil supply path to the slide groove 3b are made common to simplify the oil supply system. This has the effect of reducing manufacturing costs. The slide groove 3b extends to the outer periphery of the piston cut surface 3c. Thereby, since the movement of the cutting tool during groove processing becomes uniform, there is an effect that the shape accuracy of the groove is improved.

  Moreover, although it mentions later, it becomes an oil supply path to the piston cut surface 3c. By the way, in this embodiment, the slide shaft is set to the normal direction of the cut shaft (axis perpendicular to the swing bearing shaft). That is, the slide shaft is provided in a direction perpendicular to the two piston cut surfaces 3c parallel to the cut shaft. In this case, the pin shaft adjustment angle δ is set to 0 degree.

  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 having a cylindrical shape as a main body and having a rolling axis as a central axis and a rolling end plate 1a having a diameter larger than that of the rolling cylinder 1b are attached to the rolling cylinder 1b. Have. For this reason, the rolling end plate 1a will be in the state which protruded uniformly to the cylinder attachment surface 2a used as the lower surface part of the rolling cylinder 1b. A cylinder groove 1c having a constant width parallel to the rolling axis is provided on the upper surface side which is the side opposite to the end plate of the rolling cylinder 1b, with the cylinder groove axis orthogonal to the rolling axis 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. The piston cut surface 3c is fitted into the side surface of the cylinder groove 1c so that the rolling cylinder 1 is engaged with the revolving piston 3. Here, the turning piston 3 is inserted into the eccentric bearing 23 with the eccentric shaft 6a having a turning radius E of the crankshaft 6, and is rotated at the turning radius E by rotating the crankshaft 6, so that the cylinder groove 1c An eccentric shaft insertion hole 1d is provided at the bottom center.

  Next, the stationary cylinder 2 and the pin mechanism 5 will be described with reference to FIGS.

  The stationary cylinder 2 has a circular eccentric cylinder hole 2b having a cylinder rotation axis as a central axis in a cylinder mounting surface 2a on the lower surface. Then, a cylindrical fixing pin 5s having the pin axis as a central axis is fixedly disposed on the bottom surface of the eccentric cylinder hole 2b, and the pin mechanism 5 is provided. The pin mechanism 5 constitutes a pin slide mechanism by being inserted into the slide groove. Since the slide groove 3b provided in the orbiting piston 3 is assumed to have a pin shaft adjustment angle δ of 0, the pin shaft is installed at a position 2E away from the cylinder rotation shaft. This pin slide mechanism plays a role of defining the posture in accordance with the turning phase of the turning piston 3, and is an essential mechanism for smoothly continuing the compression operation of the RC compressor. As shown in FIG. 12, the fixing pin 5s has a through hole formed in the bottom of the eccentric cylinder hole 2b, and the fixing pin flange portion 5s1 is fixedly arranged by one or a plurality of screws.

  As a result, even if an impact load in a direction perpendicular to the axial direction is applied near the tip of the fixing pin 5s and a torque that squeezes the fixing pin 5s is applied, the screw is fixed at a position away from the pin shaft. Therefore, the opposing torque can be easily generated. Thereby, there is an effect that it is possible to avoid a risk that the fixing pin 5s drops off from the stationary cylinder 2, and it is possible to continue a reliable compression operation.

  Further, a suction hole 2s1 connected to the bottom surface and side surface of the eccentric cylinder hole 2b from the top surface and a suction groove 2s2 connected to the eccentric cylinder hole 2s1 are provided on the bottom surface of the eccentric cylinder hole 2b. These suction holes 2s1 and suction grooves 2s2 constitute a suction path 2s. Further, a discharge hole 2d that connects the top surface to the bottom surface and side surface of the eccentric cylinder hole 2b is provided.

  Further, a bypass hole 2e penetrating from the upper surface of the stationary cylinder 2 to the eccentric cylinder hole 2b is provided near the side surface of the eccentric cylinder hole 2b. In this embodiment, the number is two. A bypass valve 22 is provided on the upper surface side. 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 eccentric cylinder hole 2b to the upper part.

  Finally, the crankshaft 6 having the shaft axis as the central axis will be described with reference to FIG.

  A shaft collar portion 6c having a large diameter portion is provided at an upper portion of the shaft, and an eccentric shaft 6a having an eccentric shaft axis having an eccentric amount E with respect to the shaft axis as a central axis and a shaft neck having a smaller diameter than the eccentric shaft 6a. An eccentric portion consisting of 6d is provided. 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. A protruding pump connecting pipe 6z is fixedly disposed by press-fitting, interference fit or adhesion at the lower end 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 lateral direction. These oil supply lateral holes are installed at positions facing the bearings when the crankshaft 6 is incorporated in an RC compressor.

  Next, the structure of the compressor component demonstrated so far is demonstrated using FIG. However, only the description regarding the compression part which needs detailed description is mentioned later. First, the overall configuration of the RC compressor will be described with reference to FIG. 8, and the configuration of the compression unit requiring detailed description will be described in the latter half.

  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 6c on the collar receiving 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 6a protrudes into the cylinder groove 1c, and then the swing piston 3 is cranked so that the eccentric shaft 6a is inserted into the swing bearing 23. Install in the shaft 6. Thereby, the slewing bearing shaft of the slewing piston 3 can rotate around the eccentric shaft shaft disposed at the slewing radius E from the shaft shaft. In other words, the orbiting piston has the orbiting bearing shaft as the piston rotation axis, and the shaft axis serves as the piston orbiting shaft that causes the piston rotation axis to rotate at the orbiting radius E.

  Between the eccentric shaft 6a and the shaft collar portion 6c, a shaft neck 6d having a smaller diameter than the eccentric shaft 6a is provided 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. Thus, the cylinder groove axis and the cut axis coincide with each other, and both are perpendicular to the shaft axis, that is, the piston revolution axis.

  Next, as described above, the stationary cylinder 2 incorporating the pin mechanism 5 (the stationary cylinder 2 with the fixed pin 5s fixedly disposed) is inserted into the eccentric shaft insertion hole 1d by inserting the rolling cylinder 1b of the rolling cylinder 1 into the rolling shaft. The shaft axis (piston pivot axis) is located at the intermediate position between the cylinder pivot axis and the pin axis to the frame 4 in which the pivot piston 3, the rolling piston 1 and the crankshaft 6 are assembled as described above. Then, the cylinder bolt 90 (see FIG. 1) is closely fixed and arranged.

  As a result, the cylinder rotation axis and the pin axis are arranged on the piston rotation path circle, which is the rotation path of the piston rotation axis, and the position of the pin axis is centered on the shaft axis (cylinder rotation axis). This means that it is arranged at a position facing 180 degrees (a position where the pin axis adjustment angle δ is 0 degrees). If the stationary cylinder 2 is arranged in such a position and rotation posture, the pin mechanism 5 is automatically inserted into the cylinder groove 3b.

  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 is increased, it is necessary to increase the length of the cylinder groove 1c, and the diameter of the rolling cylinder 1b is increased. Therefore, since the diameter of the rolling cylinder 1 increases and the diameter of the stationary cylinder 2 into which the rolling cylinder 1 is incorporated increases, the diameter of the casing 8 increases and the RC compressor becomes larger in diameter. In this embodiment, as shown in FIG. 1, the shaft neck 6d is provided so that the eccentric shaft insertion hole 1d passes through the shaft neck 6d having a smaller diameter than the eccentric shaft 6a. As a result, since the eccentric shaft insertion hole 1d can be made small, an increase in the diameter of the RC compressor can be suppressed.

  Next, the configuration of the compression unit 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. From the geometrical relationship, the rotation direction of the crankshaft 6 and the rotation direction of the rolling cylinder 1 are the same. For this reason, in these drawings, since the crankshaft 6 rotates clockwise, the rolling cylinder 1 also rotates clockwise (the arrows indicating the rotation direction of the rolling cylinder 1 are shown in FIGS. 2 and 3). Therefore, when the rolling cylinder 1 is rotated clockwise, the suction chamber is provided in order to start the suction stroke of the zero-capacity working chamber (the left working chamber of the orbiting 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. Provide a suction channel. Specifically, as shown in FIGS. 2 and 3, the suction groove 2 s 2 at the bottom of the eccentric cylinder hole 2 b connected to the suction hole 2 s 1 continues 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 extended | stretched as much as possible (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 such a case, since the suction hole 2s1 and the casing 8 are close to each other, it is possible to shorten the suction pipe 50 in the RC compressor, and it is possible to suppress suction overheating and improve performance.

  By the way, in the form like the present embodiment in which the cylinder groove 1c reaches the side surface of the rolling cylinder 1b, in fact, at the timing when one of the working chambers in FIGS. It is designed not to communicate with, but to communicate after a slight rotation. This is because the piston cylindrical peripheral surface 3e is designed not to collide with the inner peripheral surface of the eccentric cylinder hole 2b. Otherwise, the piston cylindrical peripheral surface 3e will collide with the inner peripheral surface of the eccentric cylinder hole 2b, and the reliability will be impaired, and noise and vibration will increase, and the efficiency will decrease due to increased sliding loss at the collision location. This is because it occurs.

  That is, it is necessary to set a tolerance so that the piston cylindrical peripheral surface 3e does not collide with the inner peripheral surface of the eccentric cylinder hole 2b at the timing of FIGS. In other words, the tolerance setting is performed so that a gap is reliably left between the piston cylindrical peripheral surface 3e and the inner peripheral surface of the eccentric cylinder hole 2b. 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 eccentric cylinder hole 2b) is formed between the piston cylindrical peripheral surface 3e and the inner peripheral surface of the eccentric cylinder hole 2b. The

  For this reason, if both the suction passage 2s and the discharge hole 2d are connected to this working chamber, the gap between the inner peripheral surface of the piston cylindrical peripheral surface 3e and the eccentric cylinder hole 2b becomes an internal leakage flow path, and the working fluid to be discharged Returns to the suction side, causing a significant reduction in compressor efficiency and volumetric efficiency.

  Therefore, as described above, at the timing when one of the working chambers in FIGS. 2 and 3 has the volume 0, the working chamber having the volume 0 is not communicated with the suction hole 2s1, but is communicated after being slightly rotated. To design.

  Further, when the rolling cylinder 1 rotates clockwise, a sealed state in which the working chamber having the maximum volume in FIGS. 2 and 3 is not allowed to communicate with the discharge hole 2d or the suction passage 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 discharge hole 2d is provided at a position where communication starts. From that time, the compression chamber 100 becomes the discharge chamber 105, and the discharge hole 2d 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. Also, under an overcompression condition where the operating pressure ratio is equal to or less than the pressure ratio corresponding to the compression ratio 2.2, the working fluid is discharged from the bypass hole 2e through the bypass valve. In the present embodiment, the bypass hole 2e is designed to face the working chamber from the second half of the suction stroke to the entire compression stroke and the first half of the discharge stroke. Thereby, there is an effect of improving the compressor efficiency by avoiding over-compression under over-compression conditions and reducing the discharge flow path resistance. Further, since the liquid compression can be avoided including the suction stroke, there is an effect of improving the reliability of the compressor.

  Finally, the discharge hole 2d is provided at a position and a size such that the discharge hole 2d is removed from the discharge chamber 105 when the discharge stroke in which the volume of the discharge chamber 105 becomes zero (see the working chamber of volume 0 in FIGS. 2 and 3). It is done. In this case, the discharge part directly communicating with the discharge chamber 105 is the cylinder internal discharge groove 2d1 provided on the piston cylindrical peripheral surface of the eccentric cylinder hole 2b, but is not limited thereto, and the bottom of the eccentric cylinder hole 2b such as the suction groove 2s2 is used. It is good also as a groove | channel provided in. In this case, the discharge hole 2d can be set even when the specific volume ratio is large and the compression chamber 100 needs to be compressed until the volume of the compression chamber 100 is reduced at the start of the discharge stroke.

  Next, the flow of the working fluid that is a gas will be described. Here, the flow of the compression unit will be described in detail in the latter half together with the operation of the compression unit.

  The working fluid enters the compression section through a suction pipe 50 that is a suction flow path from a suction system outside the RC compressor. Therefore, the pressure is increased by the compression operation of the compression unit described later. The pressurized working fluid blows upward from the discharge hole 2d on the upper surface of the stationary cylinder 2 constituting the compression unit. Under over-compression conditions in which the operating pressure ratio is lower than the pressure ratio corresponding to the specific volume ratio of the RC compressor, the working fluid also blows out from the bypass hole 2e via the bypass valve 22.

  By the way, an upper cylinder wall 2w is arranged on the upper part of the stationary cylinder 2 so as to cover the inner side of the cylinder bolt 90 for attaching the stationary cylinder 2 to the frame 4. A discharge cover 230 is fixed on the upper surface of the cylinder upper wall 2w to cover the discharge hole 2d and the bypass hole 2e, and an upper wall groove 2w1 connecting the inner peripheral portion and the outer peripheral portion is provided at a plurality of locations on the cylinder upper wall 2w. ing.

  The working fluid blown upward from the discharge hole 2d and the bypass hole 2e once collides with the discharge cover 230, where oil in the working fluid adheres to and separates from the discharge cover, and blows out from the upper wall groove 2w1. And it collides with the inner wall of the casing cylindrical part 8a, oil is made to adhere there, and oil separation is performed again. Since the discharge pipe 55 is provided in the casing upper lid 8b, the working fluid flows to the upper side of the compression section and enters the wide casing upper chamber 120 provided there. In this case, since the flow rate of the working fluid is reduced, the remaining oil mist is allowed to settle to realize a state where the amount of oil is extremely small, and then from the discharge pipe 55 serving as a discharge flow path to the discharge system outside the RC compressor. Discharge the working fluid.

  As described above, there is no main flow of working fluid in the lower part of the compression part, but the cylinder outer peripheral gap 2g and the frame outer peripheral gap 4g which are the outer peripheral gaps of the compression part, and the cylinder outer peripheral groove 2m and the frame which are the outer peripheral grooves of the compression part A working fluid having a discharge pressure flows through the outer circumferential groove 4m. As a result, a high-pressure chamber system is realized in which the entire casing space including the lower part of the compression part is used as the discharge pressure.

  Next, the flow of the working fluid in the compression section will be described together with the operation of the compression section with reference to FIGS. 9, 10 and 11 (both sections slightly lower than the BB section in 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.

  FIG. 9 shows the state of the compression element every 45 degrees while the crankshaft 6 makes one clockwise rotation around the piston rotation axis (shaft axis, 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 view of FIG. 9 (see FIG. 10 which is an enlarged view) of FIG. 9 where the crank angle is 0 degree, the piston rotation shaft overlaps the pin shaft.

  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 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 cylinder rotation shaft 89 coincide with each other. 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 half means of the rotating piston 3 is configured by inserting a pin 5 fixedly arranged on the stationary cylinder 2 into a slide groove 3b provided on the piston upper surface 3d which is the upper surface of the rotating piston 3. This is realized by a pin slide mechanism. 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 cylinder rotation 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 pin 5 and the slide groove 3b, which are pin mechanisms. Further, the magnitude of the load is an ideal movement of the compression element that is difficult to predict that arises from the gap of each part. It causes irregular and shocking changes due to the deviation from

  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 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 exists an effect that sealing performance improves and compressor efficiency improves.

  The stroke after the second rotation will be described in the other working chamber in FIG. 9 (the right working chamber in the upper left diagram) as described above. The working chamber which has been the suction chamber 95 so far becomes a sealed space with the suction flow path 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 hole 2d before reaching the lower right view of FIG. 9 where the volume of the compression chamber 100 approaches zero, and the discharge stroke is started and the discharge pressure is reached. The fluid is discharged into the RC compressor through the discharge hole 2d.

  For example, when the volume of the compression chamber at the time of discharge becomes 1 / 2.2 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 process proceeds from the completion of the compression stroke to the start of the discharge stroke. The timing is shown enlarged in FIG. However, when the release valve operates, the discharge stroke has been completed before this arrangement.

  This discharge stroke continues until the crank angle in FIG. 9 is 360 degrees, that is, the crank angle of 0 degrees is shown in the upper left diagram. 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 casing 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 working chamber 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.

  Finally, the oil flow will be described.

  The oil in the oil storage section 125 is sent by the positive displacement oil pump 200 into the oil supply vertical hole 6b through the pump connection pipe 6z that rotates together with the crankshaft 6. Then, the oil is supplied to each bearing portion (sub-bearing 25, lower main bearing 24b, upper main bearing 24a) through the three oil supply lateral holes. In addition, oil flows into the shaft eccentric end space 115 surrounded by the crankshaft 6, the slewing bearing 23, and the slewing piston 3 from the uppermost opening of the oil supply vertical hole 6 b. As a result, the oil supply vertical hole 6b and the hole of the pump connection pipe 6z become shaft through vertical holes, the shaft eccentric end space 115 plays a role of a slide path, and oil enters the slide groove 3b of the swing piston 3 to supply the swing bearing 23. At the same time, oil is supplied to the pin slide mechanism.

  Of these, the upper main bearing 24a is supplied with oil by the upper main oil supply horizontal hole 6e and the main oil supply groove 6k. Thereafter, the gap between the shaft collar portion 6c and the collar receiving surface 4c (thrust bearing portion of the crankshaft 6) is lubricated through the collar receptacle cutout 4c1 and the lower surface portion of the shaft collar portion 6c of the oil supply main shaft groove 6k. Then, it flows into the back pressure chamber 110 formed between the swing piston 3 and the rolling cylinder 1 and the frame 4. On the other hand, the lower main bearing 24b is supplied with oil through the lower oil supply main horizontal hole 6f. Since there is no groove in the bearing, the amount of flow is small. An oil supply groove similar to the oil supply main shaft groove 6k of the upper main bearing 24a may be provided here.

  Further, the slewing bearing 23 is supplied with oil by the shaft eccentric end space 115 and the oil supply eccentric groove 6h. Thereafter, the oil flows into the back pressure chamber 110 in the same manner as the oil flowing through the upper main bearing 24a. The auxiliary bearing 25 is supplied with oil through the auxiliary oil supply lateral hole 6g. Similar to the lower main bearing 24b, the amount of flow is small because there is no groove in the bearing portion. Here, although the oil is supplied to the auxiliary bearing 25, the oil supply auxiliary lateral hole 6g may be omitted. Part of the oil discharged from the positive displacement oil supply pump 200 enters the oil supply pump shaft chamber 150 through a gap around the pump connecting pipe 6z.

  For this reason, since the oil supply pump shaft chamber 150 is filled with oil having a pressure higher than the discharge pressure, the auxiliary bearing 25 is supplied with oil. As a result, there is no need to process the refueling sub-lateral hole 6g, and the processing cost is reduced. From the above, most of the oil that has passed through the oil supply vertical hole 6 b flows into the back pressure chamber 110.

  Next, refueling to another pin slide mechanism will be described. This is performed in a thick straight oil supply vertical hole 6b and a shaft eccentric end space 115 having a large cross-sectional area and a short length. Therefore, the flow resistance is extremely small, and high-pressure oil reflecting the pressure increase by the positive displacement oil pump 200 provided at the lower end of the oil supply vertical hole 6b is supplied in abundant manner. As described above, the oil in the oil storage section 125 has a discharge pressure, so that the oil supplied to the pin slide mechanism becomes a pressure equal to or higher than the discharge pressure with a slight increase in pressure. That is, by using the oil in the oil storage section 125 as the discharge pressure, it is possible to suppress the consumption input of the positive displacement oil pump 200, and the compressor efficiency is improved.

  Thus, the oil supply vertical hole 6b realizes a shaft through-hole and the shaft eccentric end space 115 forms a slide path, and both the oil supply vertical hole 6b and the shaft eccentric end space 115 form a pin slide oil supply path. The positive displacement oil pump 200 disposed at the lower end of the pin slide oil supply passage and regarded as a part of the pin slide oil supply passage realizes a pump in the oil supply passage, and serves as a pin slide oil pressure increasing means. Accordingly, even if the working fluid leaks from a high pressure region such as the discharge chamber 105 in the vicinity of the pin slide mechanism, the pressure is at most a discharge pressure, so oil supply to the pin slide mechanism that is higher than the discharge pressure. Will not interfere.

  As described above, since oil can be constantly supplied to the pin slide mechanism, there is an effect that the risk of wear is reduced and a highly reliable RC compressor can be realized.

  Furthermore, as shown in FIG. 14, since the fixed pin vertical hole 5s3 (concave portion) and the fixed pin horizontal hole 5s5 are provided at the distal end portion of the fixed pin 5s, the slide groove that is the sliding portion of the pin slide mechanism passes through them. Oil can be directly supplied between 3b and the outer peripheral surface of the fixing pin 5s. That is, the fixed pin vertical hole 5s3 and the fixed pin horizontal hole 5s5 realize a pin oil supply path. Therefore, there is an effect that wear at this portion can be further reduced. By the way, the opening position (pin oil passage side opening) of the fixing pin 5s outer periphery of the fixing pin lateral hole 5s5 is a sliding portion (12 o'clock in FIG. 9) at a timing when the risk of wear is high (crank angle 180 degrees in FIG. 9). And the 6 o'clock direction) are slightly shifted (described at a crank angle of 180 degrees in FIG. 9 such as 1 o'clock or 7 o'clock). Thereby, since the reduction of the sliding area accompanying the opening of the fixing pin horizontal hole 5s5 can be avoided, the adverse effect of the fixing pin horizontal hole 5s5 can be eliminated, and the risk of wear can be further reduced.

  Most of the oil supplied to the pin slide mechanism is reversed in the shaft eccentric end space 115, enters the oil supply eccentric groove 6h, and is supplied to the swivel bearing 23. Thereby, since most of the oil supplied to the pin slide mechanism is oil immediately after flowing in from the oil supply vertical hole 6b, the temperature is low and the viscosity is high. Therefore, there is an effect that the risk of wear in the vicinity including the pin slide mechanism can be further reduced.

  By the way, a part of the oil supplied to the pin slide mechanism passes through the slide groove 3b and into a gap (see FIGS. 5 and 6) between the piston upper surface 3d of the turning piston 3 and the bottom surface of the eccentric cylinder hole 2b of the stationary cylinder 2. enter. This is one of the most important seal gaps that partition the suction chamber 95 and the compression chamber 100 (or the discharge chamber 105). By supplying oil to this, internal leakage and friction are reduced. Furthermore, since the slide groove 3b penetrates to the piston cut surface 3c, the other most important cylinder groove 1c side surface and the piston partitioning the suction chamber 95 and the compression chamber 100 (or the discharge chamber 105) through the slide groove 3b. Oil can be efficiently supplied to the seal gap (see FIGS. 4 and 5) of the cut surface 3c, and internal leakage and friction are reduced.

  Most of the oil flowing into these gaps enters the suction chamber 95, the compression chamber 100, and the discharge chamber 105, but some of the oil flows between the upper surface of the rolling cylinder 1b of the rolling cylinder 1 and the bottom surface of the eccentric cylinder hole 2b of the stationary cylinder 2. Enter the gap to reduce internal leakage and friction. In this way, the sealability of each part of the compression part is improved and the friction of the sliding part is reduced, contributing greatly to the internal leakage of the RC compressor and the reduction of input power. There is an effect of realizing improvement.

  By the way, as described above, most of the oil rising in the oil supply vertical hole 6 b flows into the back pressure chamber 110. Then, the oil flows into the bed back pressure chamber 110a through the bed radiation groove 4e of the bed surface 4d of the back pressure chamber 110, and then is discharged from the lower surface side of the frame 4 to the space in the casing by the oil discharge path 4x. Is done. Therefore, the back pressure that is the pressure of the back pressure chamber 110 becomes the discharge pressure that is the pressure of the casing space. That is, the oil discharge path 4x serves as a back pressure communication path. Further, since most of the opening on the back pressure chamber 110 side of the oil discharge passage 4x is provided on the highest bed surface 4d of the back pressure chamber 110, the back pressure chamber 110 and the bed back pressure chamber 110a are made up of oil of discharge pressure. It is filled. Since the lower surface of the rolling cylinder 1 is almost at the same height as the bed surface 4d, the oil in the back pressure chamber 110 comes to the lower surface of the rolling cylinder 1 in a normal case.

  Accordingly, the oil flows toward the suction chamber 95 or the compression chamber 105 having a pressure lower than the discharge pressure formed in the upper portion of the rolling cylinder 1, so that the oil flows into the seal gap of the suction chamber 95 or the compression chamber 105. The seal gap is formed by the piston lower surface 3f of the revolving piston 3 and the bottom surface of the cylinder groove 1c of the rolling cylinder 1 (see FIGS. 4 and 5), the outer peripheral surface of the rolling cylinder 1b of the rolling cylinder 1 and the eccentric cylinder hole 2b of the stationary cylinder 2. This is a seal gap between the inner peripheral surface (see FIGS. 5 and 6) and the upper surface of the rolling end plate 1a of the rolling cylinder 1 and the cylinder mounting surface 2a of the stationary cylinder 2 (see FIGS. 5 and 6). As a result, the sealing performance of each part of the compression part is improved and the friction of the sliding part is reduced, which greatly contributes to the reduction of the internal leakage of the RC compressor and the input power, thus greatly improving the compressor efficiency and volume efficiency. There is an effect of realizing.

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

  Further, the entire rear surface of the compression movable part assembly of the rotating piston 3 mounted in the rolling cylinder 1 and the cylinder groove 1c as viewed from the back pressure chamber 110 side cannot be seen through the working chamber. This is because the bottom surface of the cylinder groove 1c serves as a back pressure cover. With such a back pressure cover, the back pressure chamber 110 is used as the discharge pressure, so that the discharge pressure is constantly applied to the entire rear surface of the compression movable part assembly, while the upper surface side of the compression movable part assembly is always suctioned. In addition to the presence of the chamber 95, a compression chamber 100 having a pressure lower than the discharge pressure is formed outside the discharge stroke. In addition, although there is a sealing gap as described above on the upper surface portion (the piston upper surface 3d, the rolling cylinder 1b upper surface) of the compression movable part assembly, the average pressure in that region is the discharge pressure and the suction pressure. Intermediate pressure between. Thereby, the resultant force of the force that the compression movable part assembly receives from the surrounding oil or working fluid is always upward, and the compression movement part assembly is pressed against the stationary cylinder 2.

  As a result, the upper gap (the gap between the upper surface of the rolling cylinder 1b of the rolling cylinder 1 and the upper surface 3d of the swing piston 3 and the bottom surface of the eccentric cylinder hole 2b of the stationary cylinder 2), which is the upward seal gap of the compression movable part assembly, and the end. The plate portion gap (the gap between the upper surface of the rolling end plate 1a of the rolling cylinder 1 and the cylinder mounting surface 2a of the stationary cylinder 2) is reduced to the limit, and internal leakage is greatly reduced. Thereby, there exists a big effect that compressor efficiency and volumetric efficiency improve significantly.

  The oil flowing out from the oil discharge path 4x to the lower side of the frame 4 comes out of the rotor cup 210 that covers the periphery of the rotor 7a and is firmly fixed to the lower surface of the frame 4. Then, it travels along the outer periphery of the rotor cup 210 and falls to the stator 7b, and further passes through a hole through which the stator winding 7b2 passes and the outer stator cut surface 7b1 to reach the space below the motor 7. Then, it returns to the oil storage part 125 through the sub-frame surrounding hole 35a.

  On the other hand, the oil that has flowed into the compression section via the seal gap is mixed with the working fluid in the compression section. Then, when the working fluid enters the leakage channel during the suction, compression, or discharge stroke, an oil film is formed in the leakage channel to suppress internal leakage. Furthermore, since the leakage flow path is a location of relative movement between the compression elements, it is a sliding location, and the oil that flows in reduces friction and improves lubricity. In this way, there is an effect of improving the compressor efficiency and the volume efficiency.

  Then, as explained in the flow of the working fluid, it blows out from the discharge hole 2d and the bypass hole 2e together with the working fluid to the upper portion of the stationary cylinder 2 and adheres to the upper and lower surfaces of the discharge cover 230 and the inner surface of the casing cylindrical portion 8a. These oils pass through the cylinder outer peripheral gap 2g and the frame outer peripheral gap 4g, which are the outer peripheral clearance of the compression section, and the cylinder outer peripheral groove 2m and the outer peripheral groove 4m, which are the outer peripheral grooves of the compressing section, due to the flow of gravity and working fluid. It flows into the space below the compression section. Then, it reaches the stator 7b through the inner surface of the casing cylindrical portion 8a, the lower surface of the frame 4, and the outer peripheral surface of the rotor cup 210. Thereafter, the oil merges with the oil from the oil discharge path 4x and returns to the oil storage section 125.

  Next, a modified example of the first embodiment in which the method of attaching the fixed pin 5s, which is the pin mechanism 5, to the stationary cylinder 2 is changed from screwing (see FIG. 12) to caulking, is an enlarged longitudinal sectional view of the P part in FIG. This will be described with reference to FIG.

  Since the fixed pin small flange portion 5s1 'having a small flange portion is provided and the pin caulking hole 5s6 is provided, the description is omitted. Inserting a press jig having a tapered tip into the pin caulking hole 5s6 and pushing it into the stationary cylinder 2 completes the fixing of the fixing pin 5s, which has the effect of reducing assembly costs.

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

  Further, as shown in FIG. 14, the pin mechanism 5 of the present embodiment is provided with oil supply holes (fixed pin vertical holes 5s3 and fixed pin lateral holes 5s5) having an outlet on the outer peripheral surface in the fixed pin 5s. As shown in the 13 M section, such an oil supply hole may not be provided. The fixing pin horizontal hole 5s5 may be omitted, and only the fixing pin vertical hole 5s3 may be provided. In these cases, drilling is not necessary, and the manufacturing cost is reduced.

  Further, in this embodiment, the upper surface of the rolling end plate 1a is provided closer to the back surface of the rolling cylinder 1 than the bottom surface of the cylinder groove 1c. In other words, the bottom surface of the cylinder groove 1c is made higher than the upper surface of the rolling end plate 1a to form a step (see FIG. 4). Thus, the working chamber (suction chamber 95, compression chamber 100, discharge chamber 105) in which a gap between the outer peripheral surface of the stepped portion and the inner peripheral surface of the eccentric cylinder hole 2b is formed in the cylinder groove 1c, the back pressure chamber 110, Therefore, there is an effect of suppressing the leakage of the gap and improving the compressor efficiency. Here, although the level difference of the present embodiment is slight, if the eccentric cylinder hole 2b of the counterpart stationary cylinder 2 is made deeper as shown by the two-dot chain line, the sealing performance of the level difference portion is improved and internal leakage is caused. Is suppressed, and the compressor efficiency and the volume efficiency are improved.

  Next, the RC compressor according to the second embodiment will be described with reference to FIGS. 15 and 16.

  FIG. 15 is a longitudinal sectional view of the slide groove insertion portion of the pin slide mechanism, and is an enlarged view of the M portion in FIGS. 12 and 13. FIG. 16 is a perspective view of the slider of the pin slide mechanism. In this embodiment, the pin mechanism 5 is provided with a slider 5a that is rotatable with respect to the pin shaft, and the other parts are the same as those in the first embodiment.

  As shown in FIG. 15, the pin mechanism 5 includes a slider 5a that is rotatable with respect to a pin shaft by a slider flange 5b. The slider 5a is an element that fits into the slide groove 3b. As shown in FIG. 16, the slider 5a has a slider shaft hole 5a2 and a slider cut surface 5a1. The slider cut surface 5a1 is provided as two flat portions parallel to each other, and is a portion to be fitted into the slide groove 3b.

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

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

  Further, in this embodiment, the slider flange 5b is provided with the slider flange vertical hole 5b1 and the slider flange horizontal hole shaft 5b2, and the slider shaft hole 5a2 and the slider flange 5b slide from the shaft eccentric end space 115 filled with oil. Provide an oil supply passage that supplies oil directly to the section. Thereby, there is an effect of further reducing the risk of wear at the pin slide mechanism and further improving the reliability of the RC compressor. Of course, this oil supply passage is not necessary.

  Next, the RC compressor according to Embodiment 3 will be described with reference to FIG.

  FIG. 17 is a longitudinal sectional view of the slide groove insertion portion of the pin slide mechanism, which is an enlarged view of the M portion of FIGS. 12 and 13, and the slider rolling element 5c is placed on the slide portion of the slider shaft hole 5a2 and the slider flange 5b. Since it is the same as that of Example 2 except having inserted, description regarding the same location is abbreviate | omitted.

  Since the back of the slider 5a is reduced, the compression operation of the RC compressor becomes smoother, and the impact force applied to the pin slide mechanism is reduced, thereby improving the reliability. Further, the friction loss at the sliding portion between the slider shaft hole 5a2 and the slider flange 5b can be reduced, and the compressor efficiency is improved. In particular, when the pin slide mechanism receives a force from the compressed working fluid due to the deviation of the setting position, the friction loss at the sliding portion of the slider shaft hole 5a2 and the slider flange 5b is large, so the amount of reduction of the friction loss is also large. There is an effect of increasing the efficiency of the compressor and increasing the efficiency of the compressor.

  Here, the slider flange vertical hole 5b1 and the slider flange horizontal hole shaft 5b2 provided in the slider flange 5b may be omitted. This is because there is a gap around the slider rolling element 5c and this gap faces the shaft eccentric end space 115, and this serves as an oil supply path.

  This eliminates the need for drilling the slider flange 5b, thereby reducing the manufacturing cost.

  Next, an RC compressor according to Embodiment 4 will be described with reference to FIG.

  FIG. 18 is a perspective view of a slider of the pin slide mechanism, which is the same as that of the second or third embodiment except that a slider groove 5a3 penetrating from one end of the slider cut surface 5a1 to the other end is provided. Is omitted.

  The slide groove 3b is normally filled with oil, and the pin mechanism 5 reciprocates therein. At this time, since the pin mechanism 5 is configured to partition the slide groove 3b, the oil pressure on the side where the volume is reduced (cross hatching side in FIG. 37) of the two slide groove spaces formed by partitioning. Rises slightly.

  Thereby, oil flows into the slider groove 5a3 from the cross hatching side space of FIG. 37 to the opposite side space. As a result, oil can be supplied to the slider cut surface 5a1 abundantly, so that the friction loss between the slider cut surface 5a1 and the sliding portion of the slide groove 3b is reduced, and the compressor efficiency is improved. In addition, when the clearance between the upper and lower sides of the slider 5a is small, the amount of pressure increase of the oil in the cross hatching side space in FIG. 37 increases and wasteful work is performed. In this case, however, the pressure increase of the oil is suppressed. Thus, there is an effect of suppressing an increase in input power.

  Incidentally, a plurality of slider grooves 5a3 may be provided on each slider cut surface 5a1 instead of one. Furthermore, it is good also as the non-penetrating slider groove 5a4 which dares to stop on the way like the dashed-two dotted line of FIG. In this case, it shall stop on the way from both ends.

  As a result, there is an effect that the pressurizing action works, the holding force of the oil film increases, and the risk of wear on the slider cut surface 5a1 and the slide groove 3b can be reduced.

  Next, an RC compressor according to Embodiment 5 will be described with reference to FIG.

  FIG. 19 is an enlarged cross-sectional view schematically showing the vicinity of the surface of a rolling cylinder, a swing piston, or a stationary cylinder. The entire surface of the rolling cylinder or the swing piston (see FIGS. 4 and 5), and at least the eccentric cylinder hole 2b in the stationary cylinder. Since it is the same as that of Example 1 thru | or 4 except providing the discontinuous familiar film 85 shown by the graph of FIG. 19 in the whole area (refer FIG. 6), the description regarding the same location is abbreviate | omitted.

  As an example of the discontinuous familiar film 85, 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, high performance can be realized even if the shape accuracy of the revolving piston 3, the rolling cylinder 1 and the stationary cylinder 2 is loosened, and there is an effect of cost reduction.

  Next, an RC compressor according to Embodiment 6 will be described with reference to FIG.

  FIG. 20 is an enlarged cross-sectional view schematically showing the vicinity of the surface of a rolling cylinder, a swing piston, or a stationary cylinder. The entire surface of the rolling cylinder or the swing piston (see FIGS. 4 and 5), and at least the eccentric cylinder hole 2b in the stationary cylinder. Since it is the same as that of Example 5 except providing the discontinuous familiar film 85 shown by the graph of FIG. 20 in the whole area (refer to FIG. 6), the description regarding the similar parts is omitted.

  As an example of the continuous familiar film 86, there is a surface-modified familiar film that is immersed in a treatment agent to modify the surface. This is because, as shown in FIG. 20, the constituent precipitates on the surface of the original base material and reacts with the treatment agent to form a highly adaptable precipitated 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, an RC compressor according to Embodiment 7 will be described with reference to FIGS. 21 and 22.

  21 is a longitudinal sectional view of the lower end portion of the outer periphery of the rolling cylinder 1b of the rolling cylinder 1, which is an enlarged view of a Q portion in FIG. 1, and FIG. 22 is a perspective view of the rolling cylinder 1.

  The rolling end plate 1a of the previous embodiment (see FIG. 4) is replaced with a cylindrical rolling cylindrical end 1h, and other than this is the same as in the first to sixth embodiments, so the explanation regarding the similar parts is as follows. Omitted.

  Since the rolling cylindrical end 1h is opened to the outer peripheral side by back pressure, the rolling cylinder end 1h is biased to the inner peripheral surface of the eccentric cylinder hole 2b of the stationary cylinder 2, and the compression chamber 100 and the suction are provided above the back pressure chamber 110 and the rolling cylindrical end 1h. The sealing performance between the chamber 95 and 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.

  Further, in place of the rolling cylindrical end 1h that realizes the reduction of the gap due to the deformation to the outer periphery due to the back pressure as described above, the gap is not reduced but the gap length is increased to suppress the leakage. A variation example in which the rolling cylindrical long end 1i indicated by the chain line is used is also conceivable. In this case, even if the discharge pressure is extremely high, the rolling cylinder end portion is not pressed against the inner peripheral surface of the eccentric cylinder hole 2b, and there is an effect that the danger of a sudden increase in input can be avoided.

  Next, an RC compressor according to Embodiment 8 will be described with reference to FIGS.

  FIG. 23 is a perspective view of the rolling cylinder 1, and FIG. 24 is a top view of the rolling cylinder 1.

  The rolling end plate and the rolling cylinder of the rolling cylinder 1 of the previous embodiment (see FIG. 4) are changed to a flat plate-like separate rolling end plate 1a ′ and a cylindrical separate rolling column 1b ′, which are separated on the cylinder axis. Except for fixing with the end plate screw 1w so that the central axis of the body rolling end plate 1a ′ comes, it is the same as in the first to sixth embodiments, and thus the description of the same part is omitted.

  Flat finishing is possible for the finishing of the rolling end plate, which can improve accuracy and reduce costs. Furthermore, since the positional accuracy is not required for fixing the screw to the main body, the cost increase due to the screw fixing is limited, and the effect of reducing the manufacturing cost is produced overall. Of course, it is not limited to screw fixation, but may be welding or adhesion.

  Next, an RC compressor according to Embodiment 9 will be described with reference to FIGS. 25 and 26.

  FIG. 25 is a perspective view of the rolling cylinder 1, and FIG. 26 is a top view of the rolling cylinder 1. Since it is the same as that of Example 1 thru | or 8 except for hollowing out the inside of a thick part and providing the rolling hollow part 1v which is a hollow part, description regarding the same location is abbreviate | omitted.

  As a result, the mass and moment of inertia of the rolling cylinder 1 are reduced, so that it can be easily rotated by the orbiting piston 3. By reducing unnecessary collisions, vibration noise is reduced, wear is reduced, and reliability is improved. There is an effect that improvement of compressor efficiency and volume efficiency can be realized by forming an oil film. Moreover, when the rolling hollow portion 1v is provided at a position communicating with the discharge pressure space (back pressure chamber 110) as in the present embodiment, the outer peripheral surface of the rolling cylinder 1b slightly bulges outward due to the discharge pressure. Thereby, the gap with the inner peripheral surface of the eccentric cylinder hole 2b is reduced, and there is an effect of suppressing leakage and improving compressor efficiency and volume efficiency. Further, the side surface of the cylinder groove 1c is slightly recessed inward. As a result, the gap with the piston cut surface 3c is reduced, leakage is suppressed, and the compressor efficiency and volume efficiency are improved.

  Next, the RC compressor according to Embodiment 10 will be described with reference to FIG.

  FIG. 27 is a perspective view of the rolling cylinder 1 having a cylindrical end instead of an end plate. Except for providing a rolling outer peripheral recess 1n on the outer peripheral part of the rolling cylinder 1b, the rolling cylindrical end 1h and the rolling cylindrical long end 1i in the outer peripheral isolated region that is not connected to the operating chamber as a seal gap between the operating chamber and the working chamber. Since it is the same as that of Example 7, the description regarding the same location is abbreviate | omitted.

  Although the rolling cylinder 1 is rotating at an angular velocity that is half the rotational angular velocity of the orbiting piston 3, the outer peripheral portion is away from the cylinder rotation axis that is the center of rotation, and therefore the peripheral speed increases. Therefore, the outer peripheral surface of the rolling cylinder 1 and the inner peripheral surface of the eccentric cylinder hole 2b slide, and the friction loss due to the friction torque increases. Therefore, by providing the rolling outer peripheral recess 1n in the outer peripheral isolated region in a range that does not affect the seal of the working chamber, the sliding area can be reduced and the friction loss can be reduced. Thereby, there is an effect that the input is reduced and the compressor efficiency is improved.

  Moreover, since the rolling outer periphery dent part 1n of a present Example is extended to a lower end, a lower end part contacts the oil of the back pressure chamber 110, and oil enters the rolling outer periphery dent part 1n. Therefore, the lubricating action of the oil has the effect of further reducing friction loss and further improving the compressor efficiency. At this time, the lower end of the rolling outer periphery recessed portion 1n communicating with the back pressure chamber 110 serves as an outer periphery recessed oil introduction path. On the other hand, in order to improve the sealing performance, it is of course possible to form the lower end of the rolling outer periphery recessed portion 1n so as not to be connected to the back pressure chamber 110.

  Next, the RC compressor according to Embodiment 11 will be described with reference to FIG.

  FIG. 28 is a perspective view from below of the stationary cylinder. Since it is the same as in Examples 1 to 10 except that the cylinder inner circumferential recess 2n is provided in the inner circumferential portion of the eccentric cylinder hole 2b in the inner circumferential isolated region that is not connected to the working chamber as a seal gap with the working chamber, A description of similar parts is omitted.

  Although the rolling cylinder 1 is rotating at an angular velocity that is half the rotational angular velocity of the orbiting piston 3, the outer peripheral portion is away from the cylinder rotation axis that is the center of rotation, and therefore the peripheral speed increases. Therefore, the outer peripheral surface of the rolling cylinder 1 and the inner peripheral surface of the eccentric cylinder hole 2b slide, and the friction loss due to the friction torque increases. Therefore, by providing the cylinder inner peripheral recess 2n in the inner peripheral isolated region in a range that does not affect the seal of the working chamber, the sliding area can be reduced and the friction loss can be reduced. Thereby, there is an effect that the input is reduced and the compressor efficiency is improved.

  Further, since the cylinder inner circumferential recess 2n of the present embodiment extends to the lower end, the lower end contacts the oil in the back pressure chamber 110, and the oil enters the cylinder inner circumferential recess 2n. Therefore, the lubricating action of the oil has the effect of further reducing friction loss and further improving the compressor efficiency.

  At this time, the lower end of the cylinder inner peripheral recess 2n communicating with the back pressure chamber 110 plays a role of an inner peripheral recess oil introduction path. On the other hand, of course, the lower end of the cylinder inner circumferential recess 2n may be of a shape that does not connect to the back pressure chamber 110 in order to improve the sealing performance.

  By the way, the stationary cylinder 2 can be regarded as being composed of a plate-shaped cylinder flat plate portion and a ring-shaped cylinder annular portion when divided by a two-dot chain line of FIG. It is also conceivable to divide the cylinder at the bottom of the eccentric cylinder hole 2b along this view, divide it into a cylinder flat plate 2f and a cylinder annular body 2c, and fix them with screws or the like. In this way, the surface roughness of the bottom surface of the eccentric cylinder hole 2b that forms the most important seal gap with the piston upper surface 3d of the orbiting piston 3 can be improved very easily.

  Furthermore, since the eccentric cylinder hole 2b becomes a through hole in the cylinder annular portion 2c, the surface roughness of the inner peripheral surface of the eccentric cylinder hole 2b that forms the most important seal gap is the same as that of the outer peripheral surface of the rolling cylinder 1b of the rolling piston 1. It can be improved very easily. As a result, there is an effect that internal leakage and friction loss in these two gaps are reduced, and compressor efficiency and volume efficiency are improved. Of course, the connection between the cylinder flat plate portion 2f and the cylinder annular portion 2c is not limited to screw fixing, and may be welding or adhesion.

  Next, the RC compressor according to Embodiment 12 will be described with reference to FIG. This embodiment is an embodiment of a horizontal RC compressor in which the crankshaft 6 is horizontally arranged.

  FIG. 29 is a longitudinal sectional view across the bypass valve and the discharge flow path of the horizontal RC compressor. In order to smoothly discharge the oil from the back pressure chamber 110, the position of the oil discharge passage 4x is moved to the vicinity of the height of the central axis, and the lower upper wall groove 2w1 is prevented so that the discharge gas does not blow into the oil. Since it is the same as that of Example 1 thru | or 11 except changing the structure of the oil storage part 125 vicinity, the description regarding the same location and a simple change location is abbreviate | omitted. In other words, the position of the oil discharge path 4x is below the crankshaft 6 and above the frame 4.

  Therefore, only the configuration near the oil storage part 125 will be described below.

  An oil passage hole 35d is provided below the sub-frame 35, a slightly smaller discharge gas passage hole 35c is provided above, and an oil inflow pipe 200p having a lower end opening around the bottom is provided at the oil inlet of the positive displacement oil pump 200. Further, the discharge pipe 55 is moved to the upper part of the casing lower lid 8c. Due to the change in the vicinity of the oil storage portion 125 and the movement of the cylinder outer peripheral groove 2m and the frame outer peripheral groove 4m to the upper part, the working fluid passes from the cylinder outer peripheral groove 2m and the frame outer peripheral groove 4m to the upper stator cut surface 7b1. The gas passes through the sub-frame 35 through the discharge gas passage hole 35c and is discharged from the discharge pipe 55 to the outside of the compressor. Since this flow path is in the upper part, the working fluid can be discharged without being obstructed by the oil accumulated in the lower part.

  Here, since the discharge gas passage hole 35c has a slight flow resistance, the working fluid that has passed through the sub-frame 35 is decompressed. As a result, the oil is sucked into the oil storage part 125 from the oil passage hole 35d, the oil level of the oil storage part 125 rises, and a large amount of oil can be stored. Since the oil level on the motor 7 side is lowered to the height of the oil passage hole 35d, the motor 7 does not agitate the oil, and has an effect of suppressing the increase in the oil rate and improving the compressor efficiency by suppressing the input. .

  Next, the RC compressor according to the thirteenth embodiment will be described with reference to FIGS. 30, 31A, 32, and 33 and the reference numerals in parentheses in FIGS. 3, 6, 7, 8, 9, 10, and 11. To do.

  In this embodiment, the motor 7 and the compression portion of the upper compression vertical RC compressor shown in the first to eleventh embodiments are integrally turned upside down in the casing space, and the sub frame and the sub bearing are abolished and compressed. This is an embodiment of the lower compression vertical RC compressor in which the portion is disposed below the casing space and immersed in the oil of the oil storage portion 125 formed below to at least the height of the pin slide mechanism.

  FIG. 30 is a longitudinal sectional view across the bypass valve and the discharge flow path of the lower compression vertical RC compressor. FIG. 31A is a longitudinal sectional view of the pin mechanism attaching portion, and is an enlarged view of the S portion of FIG. 32 is a longitudinal sectional view of the vicinity of the lower part of the slewing bearing and the main bearing, and is an enlarged view of the R part in FIG. FIG. 33 is a longitudinal sectional view of the slide groove insertion portion of the pin slide mechanism, and is an enlarged view of the N portion of FIGS.

  FIG. 3 is a cross-sectional view taken along the line AA (compression chamber forming portion) in FIG. 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. 8, and the concrete structure reverses upside down. Further, FIG. 9 is an explanatory view of the compression operation using a cross section slightly shifted to the swivel piston side from the BB cross section of FIG. FIG. 10 is an enlarged view of the crank angle of 0 degrees in FIG. 9, and FIG. 11 is an enlarged view of the timing at which one working chamber shifts from the compression stroke to the discharge stroke when the bypass valve 22 does not operate. It shows a state between 180 degrees and 225 degrees.

  Among the above-mentioned changes in the arrangement, the flow path of the working fluid that enters and exits the compression unit accompanying the downward movement of the compression unit, and the pin slide mechanism and the oil supply system change to each bearing that accompany the compression unit being immersed in oil are applied. Has been. Since other than these changes are the same as those in the first to eleventh embodiments, the description regarding the same parts is omitted. Therefore, below, the flow path change of the working fluid which goes in and out of a compression part is demonstrated first, and the change of an oil supply system is demonstrated next.

  As shown in FIGS. 3, 6, 8, 9, 10, and 11, the working fluid suction side has been opened to the eccentric cylinder hole 2 b (however, the axial direction may be slightly shifted). A horizontal suction hole 2s6 similar to the suction hole 2s1 of the embodiment is provided. And at the time of an assembly, the suction pipe 50 is mounted through the casing cylindrical portion 8a.

  On the other hand, on the discharge side of the working fluid, as shown in FIGS. 1, 6, and 7, the discharge hole 2 d opening on the lower surface side of the stationary cylinder 2 and the bypass valve 22 opening are provided so as not to discharge into the oil in the oil storage portion 125. A discharge through passage 140 is provided which is covered with a hermetic discharge cover 231 and penetrates the space from the space to the upper surface of the frame 4 through the stationary cylinder 2 and the attachment surface of the frame 4. Further, an oil storage seal 215 (oil storage partition wall) that is closely fixed to the upper surface of the frame 4 is provided in the upper opening portion of the discharge through passage 140 so that oil does not enter. The crankshaft 6, the rotor 7 a, or the frame upper annular discharge port 130 around the rotating body of the main balance 80 is connected to the chamber space inside the upper portion of the oil storage limit 215.

  Next, the changed oil supply system will be described.

  First, an oil supply system for the pin slide mechanism will be described.

  As shown in FIGS. 31A and 33, the fixing pin 5 s extends through the cylinder flat plate portion of the stationary cylinder 2 to the bottom of the oil storage portion 125 by the fixing pin extension portion 5 s 2, and then the oil in the oil storage portion 125 is placed therein. A fixed pin vertical hole 5s3 is provided to hermetically connect up to the slide groove 3b of the pin slide mechanism. Here, the fixing pin 5s is a fixing pin that is fixedly disposed in the stationary cylinder 2 by press-fitting, shrink fitting, cold fitting or welding. This fixed pin vertical hole 5s3 becomes a pin slide sealed path.

  As described above, the oil level of the oil storage section 125 is adjusted so that the amount of oil to be sealed is higher than the height of the pin slide mechanism. Therefore, the pin slide mechanism includes the height of the pin slide mechanism and the oil level height. The oil whose pressure is higher than the discharge pressure is supplied by a pressure increase corresponding to the oil column weight (hereinafter referred to as “oil level differential pressure increment”). As a result, as in the case of the upper compression vertical type so far, it is possible to reliably continue the oil supply to the pin slide mechanism regardless of the pressure region in the vicinity. Since the reliability of the mechanism can be improved, there is an effect that a highly reliable RC compressor can be provided.

  Further, the fixed pin vertical hole 5s3 is in the vicinity of the pin slide mechanism and penetrates the stationary cylinder 2, and thus is a pin vicinity flow path. The pin slide mechanism, which has a high risk of wear due to the impact load, is not allowed to be in an oil-free state even for a short time, and this embodiment, which can supply oil near the pin, reduces the possibility of running out of oil. Therefore, there is an effect that the reliability of the pin slide mechanism can be improved and a highly reliable RC compressor can be provided. This time, it is a through pin hole in which an oil supply passage is provided in the fixed pin 5s itself, which can be said to be the limit in the vicinity of the pin, and the above-described reliability improvement effect is even greater.

  Next, an oil supply system for the slewing bearing 23 and the main bearing 24 will be described mainly with reference to FIG.

  The oil supplied to the slide groove 3b enters the adjacent shaft eccentric end space 115 through the fixing pin vertical hole 5s3. The oil supply lower vertical hole 6l opened there is provided with an oil supply eccentric lateral hole 6i toward the oil supply eccentric sealing groove 6h 'whose lower end is sealed. Centrifugal oil supply is performed to the oil supply eccentric sealing groove 6h 'by rotation of the crankshaft 6 through the oil supply eccentric lateral hole 6i. Thereby, the oil supply lower vertical hole 6l becomes a shaft non-penetrating vertical hole, and the oil supply eccentric horizontal hole 6i becomes a shaft turning horizontal hole. The oil that has entered the oil supply eccentric sealing groove 6 h ′ is supplied to the orbiting bearing 23 and further enters the back pressure chamber 110. Thus, the back pressure, which is the pressure in the back pressure chamber 110, is maintained at a discharge pressure or a pressure slightly higher than the discharge pressure.

  As a result, similar to the back pressure in the upper compression vertical RC compressor, the revolving piston 3 and the rolling cylinder 1 are pressed against the stationary cylinder 2 side to suppress leakage and improve the compressor efficiency and volume efficiency. There is.

  The oil that has entered the back pressure chamber 110 then enters the space where the inlet of the oil supply screw groove 6n provided in the main shaft portion of the shaft 6 opens at the upper part of the shaft collar portion 6c, and is mainly driven by the screw pump action of the oil supply screw groove 6n. After refueling the bearing 24, the bearing 24 is ejected from the upper end of the main bearing 24.

  As described above, lubrication can be performed without using a positive displacement oil pump that requires a level of power that causes a reduction in compressor efficiency to locations where lubrication is essential, such as the pin slide mechanism, the slewing bearing 23, and the main bearing 24. Therefore, there is an effect of improving the compressor efficiency. In addition, there is an effect of reducing the manufacturing cost.

  Here, as shown by a two-dot chain line in FIG. 32, instead of the oil supply eccentric horizontal hole 6i, an oil supply screw horizontal hole 6m that opens to a space where the inlet of the oil supply screw groove 6n opens may be provided. Thus, the oil supply screw side hole 6m becomes the shaft main side hole. In this case, since the oil supply to the main bearing 24 starts with almost no delay from the start of the compressor, there is an effect that the reliability of the main bearing 24 can be improved. Of course, both the oil supply eccentric horizontal hole 6i and the oil supply screw horizontal hole 6m may be provided.

  Further, even if the oil level of the oil storage part 125 is lower than the pin slide mechanism for some reason, the oil can be supplied to the pin slide mechanism by the centrifugal pump action of these oil supply lateral holes 6i, 6m. There is also an effect of improving.

  The oil spouted from the upper end of the main bearing 24 to the periphery adheres to the inner peripheral side of the main balance 80, as can be seen from FIG. And it flows down to the main balance inner periphery protrusion part 80a by gravity, and accumulates temporarily. Then, the main balance oil hole 80b leading to the outer periphery of the main balance 80 is forcibly passed by centrifugal force, adheres to the inner peripheral wall of the stator winding 7b2 and the casing cylindrical portion 8a, and becomes oil droplets as an oil storage portion. Return to 125. In other words, the oil sprayed to the periphery from the upper end of the main bearing 24 is moved toward the inner peripheral wall of the casing cylindrical portion 8a by the centrifugal force of the motor 7, passes over the upper end portion of the oil storage threshold 215, and the casing cylindrical portion It moves between the cylindrical cylindrical portion 8a and the oil storage limit 215, for example, by adhering to the inner peripheral wall of 8a and stored.

  Thereby, oil does not accumulate in the inner peripheral portion of the oil storage limit 215 where the outlet of the discharge through passage 140 opens, and there is an effect that the discharge flow is not hindered and a decrease in compressor efficiency can be avoided. Furthermore, since an increase in oil mist can also be avoided, there is an effect that the risk of a drop in the oil level of the oil storage part 125 can be reduced.

  Next, a modification in which the fixing method of attaching the fixing pin 5s, which is the pin mechanism 5, to the stationary cylinder 2 is screwed with the fixing pin flange portion 5s1 (see FIG. 31B) is also conceivable. Since this is the same as the pin mechanism attachment in the first embodiment of the upper compression vertical RC compressor, the description thereof is omitted.

  Next, an RC compressor according to Embodiment 14 will be described with reference to FIGS.

  FIG. 34 is a longitudinal sectional view of the slide groove insertion portion of the pin slide mechanism, and is an enlarged view of the N portion of FIGS. 31A and 31B. 16 and 18 are perspective views of the slider of the pin slide mechanism. This embodiment is substantially the same as the embodiment 30 except for the pin mechanism 5 provided with the slider 5c that can be rotated with respect to the pin shaft, which is employed in the embodiment 2 or 4 of the upper compression vertical RC compressor. A description of similar parts is omitted.

  In the pin mechanism 5 provided with the slider 5c rotatable with respect to the pin shaft, the oil supplying the main bearing 24 and the swivel bearing 23 passes through the fixed pin vertical hole 5s3. Therefore, the slider flange vertical hole 5b1 is the slider as the flow path. Since it is the same as the structure demonstrated in Example 2 or 4 except setting it as the form which penetrates the flange 5b, description is abbreviate | omitted.

  Next, the RC compressor according to Embodiment 15 will be described with reference to FIG.

  FIG. 35 is a longitudinal sectional view of the slide groove insertion portion of the pin slide mechanism, and is an enlarged view of the N portion of FIGS. 31A and 31B. Since it is the same as that of Example 14 except inserting the slider rolling element 5c in the sliding part of the slider shaft hole 5a2 and the fixed pin 5s, the description regarding the same location is abbreviate | omitted.

  Since the back of the slider 5a is reduced, the compression operation of the RC compressor becomes smoother, and the impact force applied to the pin slide mechanism is reduced, thereby improving the reliability.

  Next, the RC compressor according to Embodiment 16 will be described with reference to FIGS.

  FIG. 36 is an enlarged vertical cross-sectional view of the N portion of FIGS. 31A and 31B, showing a slide groove insertion portion of the pin slide mechanism. FIG. 37 is a flowchart showing the pin slide pump operation using a view seen from a cross section slightly deviated to the swivel piston side from the BB cross section of FIG. Except for causing the pin slide pump operation described in FIG. 37 by opening the pin pump hole 5s4 in a specific direction of the side surface portion sliding with the slide groove 3b of the fixed pin 5s (see FIG. 36), the thirteenth to thirteenth embodiments. 15 is the same as in FIG.

  The fixed pin 5s constituting the pin slide mechanism slides on both side surfaces of the slide groove 3b, and divides the region in the slide groove 3b into two at the two sliding portions (see FIG. 37). Of the two regions, the cross-hatched region of FIG. 37 increases the area, and the other region decreases the area conversely. The pin pump hole 5 s 4 connects the fixed pin vertical hole 5 s connected to the oil storage part 125 to the cross-hatched area increasing region and does not connect to the other area reducing region, and thus causes a pumping action to suck up oil.

  Next, the direction in which the pin pump hole 5s4 opens will be described with reference to a crank angle of 0 degrees in FIG.

  First, the direction from the cylinder rotation axis to the shaft axis (piston turning axis) is considered as the reference direction XX. And it is set as the direction rotated 90 degree | times to the turning motion rotation direction (equal to the rotation direction of the rolling cylinder 1) of the turning piston 3 centering on a pin axis with respect to this XX direction. In all of the examples shown so far including this example, the pin shaft adjustment angle δ was 0 degree. The installation direction of the pin pump hole 5s4 described above applies only when the pin shaft adjustment angle δ is zero. The general setting direction of the pin pump hole 5s4 including the case where the pin shaft adjustment angle δ is not 0 degree is set to (90 + δ) degrees around the pin axis in the turning motion rotation direction of the turning piston 3 with respect to the XX direction. Good. This direction is described in FIG.

  As described above, the operation of the pin slide mechanism can be used to raise the pressure of the oil in the oil storage portion 125 and supply the pin slide mechanism, so that the pin slide mechanism does not increase in cost. There is an effect that it becomes possible to improve the reliability of.

  Here, by narrowing the gap between the front end surface of the fixing pin 5s and the bottom surface of the slide groove 3b, the hermeticity of the cross-hatched area increasing region in FIG. 37 can be improved, and the efficiency of the above-described pin slide pump operation can be improved. Can be increased.

  Further, as can be seen from the drawing of the crank angle of 180 degrees in FIG. 37, at the timing when the location where the pin pump hole 5s4 opens becomes the sliding location between the fixed pin 5s and the slide groove, the opening of the pin pump hole 5s4 expands in the circumferential direction. If is large, it can be seen that there is a risk of reducing the efficiency of the pin slide pump operation through the cross-hatched area increasing region and the other area reducing region through the opening. For this reason, since the opening shape is a long hole shape that is long in the pin axis direction, the circumferential expansion of the opening portion of the pin pump hole 5s4 can be reduced while ensuring the opening cross-sectional area, and thus the efficiency of the pin slide pump operation is increased. be able to.

  Next, the RC compressor according to Embodiment 17 will be described with reference to FIGS.

  FIG. 38 is a longitudinal sectional view of the pin slide mechanism, which is an enlarged view of the S part in FIG. FIG. 39 is an enlarged longitudinal sectional view of the pin slide mechanism on a plane orthogonal to the section of FIG. FIG. 40 is a longitudinal sectional view of the rotating pin support portion of the pin slide mechanism, and is an enlarged view of an E portion in FIGS. Since the pin mechanism 5 is configured by the rotation pin 5r that can rotate with respect to the pin shaft, it is the same as in the thirteenth to fifteenth embodiments, and thus the description of the same portion is omitted.

  As clearly shown in FIGS. 38 and 39, the rotation pin 5r has a rotation pin extension portion 5r2 immersed in the oil storage portion 125 and a rotation pin slide portion 5r1 attached to the slide groove 3b. The rotating pin slide portion 5r1 is provided in a direction perpendicular to the pin axis. Along with the compression operation of the RC compressor, it slides back and forth in the slide groove 3b. That is, it can be considered that the slider 5a2 of the second embodiment is integrated with the pin shaft portion. Then, the rotation pin horizontal hole 5r4 passes through the rotation pin slide part 5r1, and is connected to the rotation pin vertical hole 5r3 that opens at the lower end part and communicates with the oil storage part 125.

  Further, as shown in FIG. 40, a narrow gap is provided between the rotating pin 5r and the stationary cylinder 2, so that the rotating pin 5r can be rotated, and a fixed pin oiling hole 5r5 for supplying oil to the bearing portion. A plurality of are provided. Of course, only one fixing pin oiling hole 5r5 may be provided.

  Along with the compression operation of the RC compressor, the rotation pin 5r rotates at the rotation speed of the revolving piston 3 due to the rotation torque due to the rotation pin slide portion 5r1 mounted in the slide groove 3b. Along with this, oil is jetted to the slide groove 3b through the rotary pin vertical hole 5r3 and the rotary pin horizontal hole 5r4 while being pressurized by the centrifugal pump action.

  Thereby, since the oil of the pressure more than discharge pressure can be reliably supplied to a pin slide mechanism, there exists an effect that a highly reliable RC compressor can be supplied. Further, since the oil is supplied by a centrifugal pump action, the input is not increased, the structure is simple, and the manufacturing cost can be suppressed.

  Furthermore, the amount of oil supply and the amount of pressure increase can be increased as the rotational speed increases and the risk of pin slide mechanism wear increases. Therefore, it is possible to supply an appropriate amount of oil to the pin slide mechanism in a wide range of operation, avoiding a decrease in compressor efficiency due to wasteful lubrication, and reducing the risk of wear at the pin slide mechanism and improving reliability. There is an effect that a low-cost RC compressor can be realized.

  Next, the RC compressor according to Embodiment 18 will be described with reference to FIG.

  41 is a longitudinal sectional view of the rotating pin support portion of the pin slide mechanism, and is an enlarged view of an E portion in FIGS. 38 and 39. FIG. Since it is the same as that of Example 17 except providing the rotating pin rolling element 5k between the rotating pin 5r and the stationary cylinder 2, the description regarding the same part is abbreviate | omitted.

  Since the rattling of the rotary pin slider 5a is reduced, the compression operation of the RC compressor becomes smoother, and the impact force applied to the pin slide mechanism is reduced, thereby improving the reliability. Further, the rotating pin rolling element 5k is always immersed in the oil in the oil storage section 125, and the oil is supplied to the rotating pin rolling element 5k through the rotating pin bearing lower gap 2p. Moreover, it becomes one of the pin slide oil supply paths for supplying the rotation pin bearing lower gap 2p to the pin slide mechanism. Since this is an oil supply passage close to the pin mechanism 5, it is a pin vicinity passage. Since the oil can be supplied in the vicinity of the pin, the possibility that the oil supply is cut off can be reduced, and the reliability of the pin slide mechanism can be improved.

  Finally, the RC compressor according to Embodiment 19 will be described with reference to FIGS. 42 and 43.

  FIG. 42 is a cross-sectional view of the compression unit for explaining the relationship between the installation position of the pin shaft of the pin slide mechanism and the inclination of the slide shaft, and is an enlarged view of the U portion of FIG. FIG. 43 is a detailed explanatory view of the installation position of the pin shaft, and is an enlarged view of a portion W in FIG.

  Since the pin shaft adjustment angle is the same as those in Examples 1 to 18 except that the pin shaft adjustment angle is set to δ degrees other than 0 degree, the description regarding the same parts is omitted.

  The pin shaft is arranged at a position rotated by δ degrees on the piston trajectory circle, and the slide shaft is rotated from the normal line of the piston cut surface 3c by δ / 2 degrees in the same direction as the pin shaft adjustment angle δ. As a result, similarly to the case where the pin shaft adjustment angle δ is 0, there is an effect that the operation lock can be avoided and the compression operation can be continued. Thereby, it is possible to avoid interference with elements and configurations provided in the cylinder flat plate portion such as the bypass valve 22, the suction hole 2s1, and the discharge hole 2d, and the degree of freedom of design is improved.

  However, the fact that it is best to set the pin shaft adjustment angle δ to 0 is explained in detail in the above-mentioned conventional example, and if the absolute value of the pin shaft adjustment angle δ is increased, it becomes difficult to avoid the lock phenomenon. Come. That is, by setting the pin shaft adjustment angle δ to 0, there is an effect that the compression operation is smoothed, vibration and noise are reduced, and an RC compressor having high reliability and high compressor efficiency can be realized.

  1: rolling cylinder, 1b: rolling cylinder, 1c: cylinder groove, 1d: eccentric shaft insertion hole, 2: stationary cylinder, 2d: discharge hole, 2e: bypass hole, 3: revolving piston, 3b: slide groove, 3c: piston Cut surface, 4: frame, 4x: oil discharge path, 5: pin mechanism, 5a: slider, 5b: slider flange, 5b1: slider flange vertical hole, 5b2: slider flange horizontal hole, 5c: slider rolling element, 5k: rotating pin rolling Moving body, 5r: rotating pin, 5r3: rotating pin vertical hole, 5r4: rotating pin horizontal hole, 5r5: rotating pin oiling hole, 5s: fixed pin, 5s3: fixed pin vertical hole, 5s4: pin pump hole, 5s5: fixed pin horizontal hole, 6: Crankshaft, 6a: Eccentric shaft, 6b: Lubrication vertical hole, 6d: Shaft neck, 6e: Lubrication upper main bearing hole, 6f: Lubrication Main bearing hole, 6z: pump connecting pipe, 7: motor, 7a: rotor, 7b: stator, 8: casing, 8a: casing cylindrical part, 8b: casing upper lid, 8c: casing lower lid, 35c: discharge gas passage hole 35d: oil passage hole, 50: suction pipe, 55: discharge pipe, 80: main balance, 80a: main balance inner circumferential protrusion, 80b: main balance oil hole, 95: suction chamber, 100: compression chamber, 105: Discharge chamber, 110: Back pressure chamber, 110a: Bed back pressure chamber, 115: Shaft eccentric end space, 120: Casing upper chamber, 125: Oil storage section, 130: Frame upper annular discharge port, 150: Oil supply pump shaft chamber, 200: positive displacement oil pump, 200p: oil inflow pipe, 210: rotor cup, 215: oil storage exhaust, 230: discharge cover, 231: sealed discharge cover

Claims (21)

A swivel piston having a slide groove;
A rolling cylinder having a cylinder groove;
A stationary cylinder having a fixing pin;
A piston turning drive source which is a drive source of the turning motion of the turning piston;
A drive transmission unit connecting the revolving piston and the piston revolving drive source;
A frame through which the drive transmission portion passes;
A casing having the swivel piston, the rolling cylinder, the stationary cylinder, the piston swivel drive source, and the drive transmission unit, and having an oil storage unit;
The swiveling piston, the rolling cylinder and the stationary cylinder constitute a compression part,
Between the rolling cylinder and the stationary cylinder, there are formed a suction chamber and a compression chamber which are two spaces partitioned by the revolving piston fitted in the cylinder groove,
The working fluid in the compression chamber is configured to reach a discharge pressure by the movement of the swiveling piston,
The fixing pin is fitted into the slide groove,
A pin slide oil supply passage for supplying oil from the oil storage section to the fixed pin and the slide groove;
A rolling cylinder positive displacement compressor having a configuration in which a pressure of oil supplied to the fixed pin and the slide groove at the outlet of the pin slide oil supply passage is equal to or higher than the discharge pressure.   The rolling cylinder type positive displacement compressor according to claim 1, wherein the pressure on the upper surface of the oil accumulated in the oil storage section is set to the discharge pressure by the working fluid flowing out from the compression chamber.   The rolling cylinder type positive displacement compressor according to claim 2, wherein the compression unit is disposed above the piston rotation drive source.   The rolling cylinder type positive displacement compressor according to claim 2, wherein the compression unit, the piston turning drive source, and the drive transmission unit are arranged in a horizontal direction. In addition, it has a fuel pump,
The rolling cylinder type positive displacement compressor according to any one of claims 2 to 4, wherein the oil pump increases pressure of oil in the pin slide oil supply passage.   The rolling cylinder positive displacement compressor according to claim 5, wherein the oil supply pump is a positive displacement pump. The drive transmission unit includes a crankshaft,
The rolling cylinder type positive displacement compressor according to claim 5 or 6, wherein an oil supply passage penetrating in a rotation axis direction is provided inside the crankshaft.   The rolling cylinder positive displacement compressor according to any one of claims 5 to 7, wherein a distal end portion of the fixing pin is provided with a recess that constitutes an oil supply passage.   The rolling cylinder type positive displacement compressor according to claim 8, wherein an oil supply passage for supplying oil to the revolving piston is provided between the concave portion of the fixed pin and a side surface portion of the fixed pin. A slider that is rotatable with respect to the fixed pin is attached to the tip of the fixed pin,
The rolling cylinder type positive displacement compressor according to any one of claims 5 to 9, wherein an oil supply passage is provided in an inside or a side portion of the slider.   The rolling cylinder positive displacement compressor according to any one of claims 5 to 10, wherein an oil discharge passage is provided in the frame. A swivel piston having a slide groove;
A rolling cylinder having a cylinder groove;
A stationary cylinder having a fixed or rotating pin;
A piston turning drive source which is a drive source of the turning motion of the turning piston;
A drive transmission unit connecting the revolving piston and the piston revolving drive source;
A frame through which the drive transmission portion passes;
A casing having the swivel piston, the rolling cylinder, the stationary cylinder, the piston swivel drive source, and the drive transmission unit, and having an oil storage unit;
The swiveling piston, the rolling cylinder and the stationary cylinder constitute a compression part,
Between the rolling cylinder and the stationary cylinder, there are formed a suction chamber and a compression chamber which are two spaces partitioned by the revolving piston fitted in the cylinder groove,
The working fluid in the compression chamber is configured to reach a discharge pressure by the movement of the swiveling piston,
The fixed pin or the rotating pin is fitted into the slide groove,
A pin slide oil supply passage for supplying oil in the oil storage section to the fixed pin or the rotation pin and the slide groove;
The oil supplied to the fixed pin or the rotation pin and the slide groove has a configuration in which the pressure at the outlet of the pin slide oil supply path is equal to or higher than the discharge pressure,
The pressure on the upper surface of the oil accumulated in the oil reservoir is the discharge pressure by the working fluid flowing out of the compression chamber,
The said compression part is a rolling cylinder type positive displacement compressor arrange | positioned under the said piston turning drive source. Furthermore, it has an oil storage limit,
The oil ejected between the piston rotation drive source and the compression part has a configuration of being stored between the oil storage limit and the casing.
The rolling cylinder type positive displacement compressor according to claim 12, wherein an upper surface of the stored oil is configured to be positioned above the compression section.   The rolling cylinder type positive displacement compressor according to claim 12 or 13, wherein an oil supply path is provided in the drive transmission portion located between the piston rotation drive source and the compression portion.   The rolling cylinder type positive displacement compressor according to any one of claims 12 to 14, wherein an oil supply passage is provided inside the fixed pin or the rotary pin.   The rolling cylinder type positive displacement compressor according to claim 15, wherein the fixed pin or the rotating pin has a configuration extending toward a bottom portion of the oil storage portion.   An oil supply path for supplying oil to the revolving piston is provided between the oil supply path provided inside the fixed pin or the rotary pin and a side surface portion of the fixed pin or the rotary pin. Item 17. The rolling cylinder type positive displacement compressor according to Item 15 or 16.   The rolling piston type positive displacement compressor according to any one of claims 1 to 17, wherein a rolling outer circumferential recess is provided on a side surface of the rolling cylinder.   The rolling piston positive displacement compressor according to any one of claims 1 to 18, wherein a cylinder inner peripheral recess is provided on an inner peripheral surface of the stationary cylinder.   The rolling piston type positive displacement compressor according to any one of claims 1 to 19, wherein the orbiting piston, the rolling cylinder, and the stationary cylinder are formed of cast iron or aluminum alloy. Between the swiveling piston and the frame, there is a back pressure chamber,
The back pressure communication path which connects the casing space which is the inside of the said casing, and the said back pressure chamber is provided so that the back pressure which is the pressure of the said back pressure chamber may be made into discharge pressure. The rolling cylinder type positive displacement compressor described in the paragraph.

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