WO2016067355A1

WO2016067355A1 - Rolling cylinder type displacement compressor

Info

Publication number: WO2016067355A1
Application number: PCT/JP2014/078552
Authority: WO
Inventors: 坪野　勇; 柳瀬　裕一
Original assignee: 株式会社日立製作所
Priority date: 2014-10-28
Filing date: 2014-10-28
Publication date: 2016-05-06
Also published as: CN107076145A; JP6294974B2; CN107076145B; JPWO2016067355A1

Abstract

A rolling cylinder type displacement compressor according to the present invention is provided with a rotary drive source, a compression unit, and an oil storage unit. The compression unit includes a rolling cylinder (1) having a cylinder groove, a circling piston (3) slidably accommodated in the cylinder groove, and a stationary cylinder (2) having an eccentric cylinder hole in which the rolling cylinder is rotatably accommodated. To the eccentric cylinder hole of the stationary cylinder, a fixed pin (5) having a center line different from a shaft axis is attached. The circling piston has a slide groove (3b). The fixed pin has such a configuration as to be slidably fitted to the slide groove, and is configured in such a manner that the autorotation of the circling piston and the rotation of the rolling cylinder are synchronized. Lubricating oil in the oil storage unit is supplied to the fixed pin and the slide groove. As a result, in the case where a pin mechanism is applied to the rolling cylinder type displacement compressor, the lubricating oil can be sufficiently supplied to the pin mechanism, so reliability of the pin mechanism can be improved.

Description

Rolling cylinder positive displacement compressor

The present invention is a compressor including three pivoting pivoting pistons, a rolling cylinder that rotates along with the pivoting piston, and a stationary cylinder incorporating them, the working fluid being a working fluid by these compression elements. The present invention relates to a rolling cylinder positive displacement compressor which performs compression of a certain gas.

Japanese Patent Application Laid-Open No. 2010-185358 (Patent Document 1) discloses a means for solving the problem of pump operation locking in a rolling cylinder positive displacement pump. In the positive displacement pump described in Patent Document 1, the working fluid is liquid oil, maintains the rotation of the swing piston and rotation of the rolling cylinder, and defines the swing speed of the swing piston to twice the rotation speed of the rolling cylinder. A rotation regulation means is provided. The rotation control means includes rotation synchronization means for synchronizing rotation of the rotation piston and rotation of the rolling cylinder, and piston rotation control means for setting the rotation speed of the rotation piston to twice the rotation speed. And a rotation synchronization means provides the turning piston with the side flat part which carries out sliding contact with two side faces of a pump groove, respectively. Further, the piston rotation regulating means is configured to fit the position fixed cylinder into the guide groove.

On the other hand, as a conventional example of a rolling cylinder type positive displacement compressor assumed to be used for a refrigeration cycle apparatus, there is JP-A-2011-17300 (Patent Document 2). Patent Document 2 includes two suction / discharge mechanisms for suctioning and discharging a refrigerant by reciprocating the piston in a piston chamber provided in a rotating cylinder, and the cylinder is pivoted by back pressure of discharge pressure. A compressor is disclosed that eliminates the need for managing the clearance between the partitioning member and the end face of the cylinder by biasing in a direction. In this conventional example, the compression operation is smoothly continued by combining another rolling cylinder compressor with different rotational phase.

JP, 2010-185358, A JP, 2011-17300, A

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

The compressor described in Patent Document 2 is different from the system using the rotation regulating means described in Patent Document 1. That is, two compression mechanism parts having different rotational phases are essential. For this reason, the volume of the whole compressor increases and the number of parts also increases. Therefore, there is a limit in improvement in terms of the compactness of the compressor. Furthermore, the assembly which strictly defines the rotational phase difference of the two compression mechanism parts becomes essential, and the deterioration of the assemblability becomes a problem.

In the case where the pin mechanism described in Patent Document 1 is applied to a rolling cylinder type compressor, it is necessary to provide a means for supplying oil to the pin mechanism in order to use the working fluid as a gas. Conventionally, there is no example which applied the said pin mechanism to a compressor.

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

The rolling cylinder positive displacement compressor according to the present invention comprises a crankshaft having an eccentric shaft with a shaft axis as a rotation center, a frame for supporting the crankshaft, a rotational drive source for applying rotational drive torque to the crankshaft, and operation. A compression unit includes a compression unit that sucks, compresses and discharges fluid, and an oil storage unit, and the compression unit includes a rolling cylinder having a cylinder groove, a pivoting piston slidably accommodated in the cylinder groove, and a rolling cylinder. And a stationary cylinder having an eccentric cylinder hole which can be accommodated, wherein a space surrounded by the rolling cylinder, the orbiting piston and the stationary cylinder is a suction chamber, a compression chamber and a discharge chamber as the rolling cylinder and the orbiting piston rotate. The eccentric shaft has a center line different from the shaft axis, and the pivoting piston A rotatable pin is disposed about the center line of the center shaft, revolves according to the rotation of the crankshaft, and a stationary pin having a center line different from the shaft axis is attached to the eccentric cylinder hole of the stationary cylinder. It has a slide groove, and the fixing pin has a configuration slidably fitted in the slide groove, and the intersection of the bottom surface of the eccentric cylinder hole and the center line of the fixing pin, the bottom surface of the eccentric cylinder hole and the rolling cylinder So that the middle point of the line connecting the centerline of the cylinder and the centerline of the line coincides with the intersection of the bottom of the eccentric cylinder hole and the centerline of the shaft axis, and these three centerlines are parallel to each other It is arranged so that the rotation of the orbiting piston is synchronized with the rotation of the rolling cylinder, and the rotation angular velocity of the orbiting piston is adjusted to half the rotational angular velocity of the crankshaft. , Constructed so that the pressure oil storage portion is equal to the pressure in the discharge chamber, and, by providing a Aburaren passage connecting the oil storage portion and the slide groove, and supplies the lubricating oil of the oil storage portion to the fixing pin and the slide groove.

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

FIG. 2 is a longitudinal sectional view across the bypass valve and the discharge flow path of the rolling cylinder positive displacement compressor according to the first embodiment. FIG. 2 is a cross-sectional view taken along line AA of FIG. FIG. 2 is a cross-sectional view taken along the line BB in FIG. FIG. 1 is a perspective view showing a rolling cylinder of a rolling cylinder positive displacement compressor according to a first embodiment. FIG. 2 is a perspective view showing a swing piston of the rolling cylinder positive displacement compressor according to the first embodiment. FIG. 3 is a bottom view showing a stationary cylinder on which the fixing pin of the rolling cylinder positive displacement compressor according to the first embodiment is mounted. FIG. 1 is a perspective view showing a frame of a rolling cylinder positive displacement compressor according to a first embodiment. FIG. 2 is an exploded perspective view showing a configuration of a compression unit of the rolling cylinder positive displacement compressor according to the first embodiment. FIG. 7 is a flow diagram showing the compression operation of the rolling cylinder positive displacement compressor according to the first embodiment, using a view seen from a cross section slightly lower than the B-B cross section of FIG. 1; It is an expanded sectional view which shows the detail of arrangement | positioning in the crank angle 0deg of FIG. FIG. 10 is an enlarged cross-sectional view showing an arrangement between a crank angle of 180 degrees and a crank angle of 225 degrees in FIG. 9 where one working chamber of the rolling cylinder positive displacement compressor according to the first embodiment shifts from the compression stroke to the discharge stroke. It is an expanded cross-sectional view which shows the M section of FIG. FIG. 13 is a cross-sectional view taken along the line O-G of FIG. FIG. 3 is an enlarged cross-sectional view schematically showing the vicinity of the surface of a rolling cylinder or a orbiting piston of the rolling cylinder positive displacement compressor according to the first embodiment. FIG. 8 is an enlarged cross-sectional view schematically showing the vicinity of the surface of a rolling cylinder or a orbiting piston of the rolling cylinder positive displacement compressor according to the second embodiment. It is an expansion cross-sectional view which shows the part applicable to the M section of FIG. 3 in the rolling cylinder type positive displacement compressor which concerns on Example 3. FIG. FIG. 17 is a cross-sectional view taken along the line O-G of FIG. It is an expansion longitudinal cross-sectional view which shows the part applicable to the P section of FIG. 1 in the rolling cylinder type positive displacement compressor which concerns on Example 4. FIG. It is an expansion longitudinal cross-sectional view which shows the part applicable to the P section of FIG. 1 in the rolling cylinder type positive displacement compressor which concerns on Example 5. FIG. FIG. 18 is an enlarged perspective view showing a slider in a rolling cylinder positive displacement compressor according to a fifth embodiment; It is an expansion longitudinal cross-sectional view which shows the part applicable to Q part of FIG. 1 in the rolling cylinder type positive displacement compressor which concerns on Example 6. FIG. It is a perspective view showing a rolling cylinder with a cylinder end of a rolling cylinder type displacement type compressor concerning Example 6.

The present invention is a compressor including three pivoting pivoting pistons, a rolling cylinder that rotates along with the pivoting piston, and a stationary cylinder incorporating them, the working fluid being a working fluid by these compression elements. The present invention relates to a rolling cylinder positive displacement compressor which performs compression of a certain gas. And, in particular, in order to continue the compression operation smoothly, it comprises rotation synchronization means for synchronizing the rotation speeds of the swing piston and the rolling cylinder, and rotation half means for defining the rotation speed of the swing piston to half the swing speed. The present invention relates to a rolling cylinder positive displacement compressor.

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

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

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

In the rolling cylinder positive displacement compressor, the oil communication passage may be a separately provided pipe, but it is preferable to use an oil supply vertical hole penetrating the crankshaft and the eccentric shaft, and a hole communicating from the oil reservoir to the slide groove. . This eliminates the need for additional piping for refueling. In addition, by providing the crankshaft or the like with a horizontal hole that communicates with the oil supply vertical hole as appropriate, the oil supply to the bearing or the like becomes easy.

In the rolling cylinder positive displacement compressor, the pivoting piston has two piston cut surfaces parallel and flat to each other, and the cylinder grooves of the rolling cylinder are two inner side surfaces parallel to each other and flat It is desirable to have a configuration in which two piston cut surfaces are slidably fitted between the two inner side portions. This ensures synchronization of the rotational speeds of the pivoting piston and the rolling cylinder.

The rolling cylinder positive displacement compressor has a suction chamber for suction pressure, and a compression chamber and a discharge chamber for raising the pressure to the discharge pressure in the vicinity of the pin mechanism, for the purpose of compression. Therefore, in order to reliably supply the pin mechanism, it is necessary to supply oil at least at the discharge pressure. By doing this, the reliability of the pin mechanism can be improved, but on the other hand, the discharge pressure, which is the maximum pressure in the compressor, is in the vicinity of the pin mechanism. And there is a problem that the gap widens.

As a result, the axial clearance between the orbiting piston and the stationary cylinder, which is the clearance closest to the pin mechanism, is also enlarged. Since this clearance is a seal between the compression chamber or the discharge chamber and the suction chamber, the leakage increases due to the expansion of the clearance. Similarly, the axial clearance between the adjacent rolling cylinder and the stationary cylinder also increases and leakage increases. Furthermore, since the working fluid is a gas, an increase in leakage occurs. Furthermore, since the purpose is compression, the pressure difference between the suction chamber and the compression chamber or the discharge chamber increases, and the amount of leakage further increases. This results in the problem of a significant reduction in compressor efficiency.

In the case of compression of a gas which is a compressible fluid, it is desirable to provide a back pressure supporting means from the viewpoint of improving the sealing performance.

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

In the rolling cylinder positive displacement compressor, it is preferable that a back pressure valve be attached to a flow passage communicating the compression chamber with the back pressure chamber. As a result, since the setting of the pressure difference between the compression chamber and the back pressure chamber is performed by the back pressure valve, the inner diameter of the flow path can be increased. For this reason, the drill blade used at the time of preparation of a flow path can be made thick, processing becomes easy, and processing cost can be reduced. In addition, since it is possible to bias the swinging piston and the rolling cylinder with a pressure close to the minimum necessary pressure to bias the stationary cylinder, it is possible to reduce the sliding loss generated with the biasing. This also contributes to the improvement of the compressor efficiency.

In the rolling cylinder positive displacement compressor, the number of compression parts can be one. In other words, it is not necessary to make another compression part with different rotational phase overlap. Thereby, a compact rolling cylinder type displacement compressor can be obtained.

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

In the rolling cylinder positive displacement compressor, preferably, the rolling cylinder has an eccentric shaft insertion hole, and the pivot piston is configured to close the eccentric shaft insertion hole. This makes it possible to ensure the airtightness of the compression section.

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

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

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

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

In the rolling cylinder positive displacement compressor, preferably, a step is provided between the bottom of the cylinder groove and the end plate front surface which is the cylinder groove side of the rolling end plate. Thereby, the sealability of the compression part can be improved.

In the rolling cylinder positive displacement compressor, the rolling cylinder may include a rolling cylinder having a cylinder groove and a rolling cylinder end having a diameter equal to that of the rolling cylinder. As a result, the diameter of the compression portion can be reduced, and the sealability can be improved.

In the rolling cylinder positive displacement compressor, it is preferable that a compatible film is provided on the surface of at least one of the rolling cylinder and the orbiting piston. As a result, high performance can be realized even if the dimensional accuracy of the orbiting piston is loosened, so that the manufacturing cost can be reduced.

Hereinafter, a rolling cylinder positive displacement compressor according to the present invention will be described in detail with reference to the drawings, using a plurality of embodiments. In the respective drawings, the same parts will be described using the same drawings. In addition, the same reference numerals in the drawings of the respective embodiments indicate the same or equivalent parts, and duplicate explanations will be omitted. Moreover, in the following description, although the expression including the direction such as the upper surface or the lower surface may be expressed in the state of being installed vertically in the figure, the actual installation is not limited to the direction expressed here .

A rolling cylinder positive displacement compressor (hereinafter abbreviated as an RC compressor) according to a first embodiment will be described with reference to FIGS. 1 to 14. FIG. 1 is a longitudinal sectional view of the RC compressor, and is a longitudinal sectional view passing through C1-C2-O-C3 of the transverse sectional view (FIGS. 2 and 3) in AA or BB shown in the figure. Here, C2 is at two places in FIGS. 2 and 3, which means that the space between two C2 is omitted. 2 and 3 are a sectional view taken along the line AA (compression chamber forming part) and a sectional view taken along the line BB of FIG. 1 (an axial gap between the stationary cylinder, the orbiting piston and the rolling cylinder). Here, in FIG. 3, the suction groove 2s2 immediately above the B-B cross section is illustrated by a two-dot chain line. 4 and 5 are perspective views of the rolling cylinder and the orbiting piston, respectively. 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 put these and the crankshaft together is FIG. And FIG. 9 is a compression operation explanatory view using a cross section slightly lower than the cross section BB of FIG. Here, in FIG. 9, the suction groove 2s2 immediately above the cross section BB is illustrated by a broken line. FIG. 10 is an enlarged view of the crank angle 0 degree of FIG. This is the timing at which the working chamber having a volume of 0 transitioning from the discharge stroke to the suction stroke and the working chamber having the largest volume moving from the suction stroke to the compression stroke coexist. FIG. 11 is an enlarged view of a timing at which one working chamber shifts from the compression stroke to the discharge stroke, and shows a state in which the crank angle in FIG. 9 is between 180 degrees and 225 degrees. 12 is an enlarged cross-sectional view of the M portion of FIG. 3 in which the back pressure flow path is disposed, and FIG. 13 is an OG longitudinal cross-sectional view of FIG. Finally, FIG. 14 is an enlarged cross-sectional view near the surface of the rolling cylinder or pivoting piston.

First, after describing the entire configuration excluding the inside of the compression unit of the RC compressor, the flows of working fluid and oil outside the compression unit will be described. Next, the configuration of the compression unit and the flow of working fluid and oil will be described in detail.

First, the entire configuration excluding the inside of the compression unit will be described with reference to FIG. The compression part is covered with a stationary cylinder 2 at the upper part and a frame 4 at the lower part, and a crankshaft 6 rotatably supported by a main bearing 24 comprising an upper main bearing 24a and a lower main bearing 24b provided on the frame 4 There is. The motor 7 is provided on the crankshaft 6 while the compression portion is fixed to the chamber cylindrical portion 8a by welding or the like. The motor 7 is composed of a stator 7 b fixedly arranged in the chamber cylindrical portion 8 a and a rotor 7 a fixedly arranged in the crankshaft 6. Here, a main balance 80 is fixed to the upper part and a counter balance 82 is fixed to the lower part of the rotor 7a. These, together with the shaft balance 81 fixedly arranged on the crankshaft 6 described in the explanation of the compression section, play a role of dynamically balancing the unbalance of the compression element (pivotal piston 3) that pivots in the compression operation.

The auxiliary bearing 25 is composed of a ball 25 a and a ball holder 25 b which rotatably supports the ball 25 a in all directions. After the lower part of the crankshaft 6 is inserted into the ball 25a and the ball 25a is attached to the ball holder 25b, the ball holder 25b is fixed and arranged on the lower frame 35 welded to the chamber cylindrical portion 8a. Thus, the auxiliary bearing 25 rotatably supports the lower portion of the crankshaft 6. Further, the fueling piece 6x is press-fitted to the lower end of the crankshaft 6. The crankshaft 6 is provided with an oil supply vertical hole 6b penetrating the center in the central axis direction. Further, the crankshaft 6 is provided with oil supply horizontal holes (an oil supply auxiliary horizontal hole 6g, an oil supply lower main horizontal hole 6f, an oil supply upper main hole 6e) connected to the auxiliary bearing 25, the lower main bearing 24b and the upper main bearing 24a.

In the present specification, the "center line" refers to a straight line passing through the center of a member having a cylindrical or cylindrical shape. In the following, "central axis" or "axis" may be used in the sense of "central line".

A chamber lower lid 8c is attached by welding to a lower portion of the chamber cylindrical portion 8a. Here, oil is sealed at an appropriate stage of the RC compressor assembly, and an oil storage portion 125 for storing oil is formed near the lowermost chamber lower lid 8c. The oil supply piece 6x is always immersed in the oil of the oil reservoir 125. The oil of the oil storage portion 125 is fed to each portion through the oil supply piece 6x, the oil supply vertical hole 6b of the crankshaft 6, and the oil supply horizontal hole.

Furthermore, a chamber upper lid 8b is welded to the upper portion of the chamber cylindrical portion 8a to form a sealed chamber 8 (described in FIGS. 12 and 13) together with the chamber lower lid 8c. A suction pipe 50 for introducing the working fluid from the outside to the compression section provided inside the sealed chamber 8 is provided on the chamber upper lid 8b. Furthermore, in the chamber upper lid 8b, a discharge pipe 55 for discharging the working fluid pressurized in the compression section 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 is provided to which the motor wire 7b3 connected thereto is connected.

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

Next, the flow of oil will be described. As described above, the oil reservoir 125 is connected to each bearing by the oil supply pipe 6x, the oil supply vertical hole 6b, the oil supply horizontal hole 6g, the oil lower main horizontal hole 6f, and the oil upper main horizontal hole 6e constantly immersed in the oil reservoir 125. A refueling channel is provided. As described above, since the pressure in the oil reservoir 125 is a discharge pressure, the oil in the oil reservoir 125 also becomes the discharge pressure. As will be described in detail in the description of the compression section later, a back pressure chamber 110 is provided for holding the outlet side of the oil from the main bearing 24 and the turning bearing 23 at a back pressure intermediate between the discharge pressure and the suction pressure. Oil is supplied to the main bearing 24 and the orbiting bearing 23 by the differential pressure between the pressure and the back pressure. Further, oil is supplied from the auxiliary bearing 25 by centrifugal oil supply from the oil supply auxiliary horizontal hole 6g, and the oil after lubrication returns directly to the oil storage portion 125.

On the other hand, after the main bearing 24 and the orbiting bearing 23 are lubricated and the oil entering the back pressure chamber 110 lubricates and seals each part in the compression part, together with the working fluid, from the discharge flow path 2d to the inside of the RC compressor It is discharged. Here, among the oil supply paths in the compression unit, only the oil supply path passing through the back pressure chamber 110 has been described, but the present invention is not limited thereto, and other oil supply paths may be present. However, in the final stage, the fluid is discharged into the RC compressor from the discharge flow path 2d together with the working fluid. These will be described in detail in the description of the compression section later.

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

Next, the configuration of the compression unit will be described in detail using FIGS. 1 to 14.

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 to which the stationary cylinder 2 is attached later is a top surface, and a main bearing hole 4b is provided at the center. An upper main bearing 24a and a lower main bearing 24b (see FIG. 1) are press-fit into the main bearing hole 4b to form a main bearing 24 for rotatably supporting the crankshaft 6. A shaft thrust surface 4c is provided around the upper surface of the main bearing hole 4b, and a shaft thrust surface groove 4c1 serving as an outlet for oil that lubricated the main bearing 24 is provided at one or more locations. Then, a bed surface 4d on which the rolling cylinder 1 is mounted is provided at a position surrounding the shaft thrust surface 4c. The bed surface 4d is provided with a bed radial groove 4e and a bed peripheral groove 4f, which are passages of oil. On the other hand, on the outer periphery of the frame 4, as described above, an oil flow lower cut surface 4g which is a passage of oil separated from the working fluid is provided.

Next, the orbiting piston 3 will be described with reference to FIG. The swing piston 3 has a configuration in which a swing bearing hole 3a is provided at the center. The pivot bearing 23 is press-fit into the pivot bearing hole 3a. Further, on the side surface of the orbiting piston 3, two parallel piston cut surfaces 3c and two cylindrical peripheral surfaces 3e whose centers are offset from each other are provided. Furthermore, the upper and lower surfaces are provided with a piston upper surface 3d and a piston lower surface 3f which are flat surfaces parallel to each other. Among these, the piston upper surface 3d is provided with a slide groove 3b having a central axis that is a slide axis that intersects the piston rotation axis, which is the central axis of the orbiting bearing 23, and is orthogonal to the piston cut surface 3c. The slide groove 3b is set to a depth which communicates with the orbiting bearing hole 3a. Moreover, the slide groove 3b is extended to the outer periphery of the piston cut surface 3c. As a result, the movement of the cutting tool at the time of grooving becomes uniform, so that the shape accuracy of the groove is improved.

Further, over the entire surface of the orbiting piston 3, a discontinuous familiar film 85 is provided which becomes discontinuous with the base material as shown in FIG. As an example of such a film, when the base material is an aluminum alloy, there is a film formed by adding a material different from the base material, such as nickel phosphorus plating, to the surface. This makes it possible to provide a highly conformable film on the swing piston 3 because an optimum conformable film can be selected with almost no restriction regardless of the base material. Therefore, high performance can be realized even if the shape accuracy of the orbiting piston 3 is loosened, so there is an effect of cost reduction.

Next, the rolling cylinder 1 will be described with reference to FIG. The rolling cylinder 1 basically has a configuration in which a rolling cylinder 1b and a rolling end plate 1a having a larger diameter than the rolling cylinder 1b are combined. For this reason, the rolling end plate 1a is in a state of being protruded uniformly to the lower surface portion of the rolling cylinder 1b. Then, on the upper surface side of the rolling cylinder 1b, a cylinder groove 1c having a cylinder axis orthogonal to the rolling cylinder axis which is a central axis of the rolling cylinder 1 as a central axis is provided.

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 cylinder 1b and the rolling end plate 1a. The cylinder groove 1c extends to the outer periphery of the rolling cylinder 1b. As a result, the movement of the cutting tool at the time of grooving becomes uniform, so that the shape accuracy of the groove is improved. Then, the piston cut surface 3c is gap-fitted to the side surface of the cylinder groove 1c, and the rolling cylinder 1 is engaged with the orbiting piston 3. Here, since the orbiting piston 3 is caused to pivot by the crankshaft 6, an eccentric shaft insertion hole 1d is provided at the center of the bottom of the cylinder groove 1c. Further, as in the case of the orbiting piston 3, an additive familiar film 85 as shown in FIG. 14 may be provided on the entire surface of the rolling cylinder 1. Thereby, the same action and effect as in the case where the additive familiar film 85 is provided on the orbiting piston 3 can be obtained.

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

The stationary cylinder 2 is basically cylindrical in shape, and has a circular cylinder hole 2b (eccentric cylinder hole) formed in the cylinder mounting surface 2a on the lower surface. Furthermore, as the pin mechanism, the simplest fixing pin 5 is fixedly disposed at a position away from the center of the cylinder hole 2b by 2E in the cylinder hole 2b. The fixing pin 5 has a small hole at the bottom of the cylinder hole 2b and is press-fitted thereto. As another arrangement method of fixing pin 5, adhesion, welding, screwing, etc. may be mentioned. Further, a suction hole 2s1 connected from the upper surface to the cylinder hole 2b and a suction groove 2s2 on the upper surface of the cylinder hole 2b connected to the cylinder hole 2s are provided. The suction passage 2s is configured by the suction hole 2s1 and the suction groove 2s2. Further, the cylinder outer discharge groove 2d3 in the vertical direction is provided on the outer peripheral side surface, the cylinder inner discharge groove 2d1 is provided on the cylindrical peripheral surface of the cylinder hole 2b, and the cylinder discharge hole 2d2 connecting these two discharge grooves is provided to constitute the discharge flow passage 2d. .

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

Furthermore, a back pressure direct current passage 200 is provided (the back pressure valve passage indicated by reference numeral 210 is neglected here because it is the third embodiment). The back pressure direct current passage 200, which will be described in detail later, is a connection of the compression chamber side back pressure vertical hole 2h1, the back pressure horizontal hole 2h2, and the back pressure chamber side back pressure vertical hole 2h3. It is a flow path connecting the compression chamber 100 and the back pressure chamber 110 provided on the back side of the orbiting piston 3 and the rolling cylinder 1. This has the role of introducing an intermediate pressure from the compression chamber 100 into the back pressure chamber 110, the role of flowing out the oil flowing into the back pressure chamber 110 into the compression chamber 100, and promoting oil circulation in the compression section. It also plays a role in improving sealing performance in the compression chamber 100 by refueling the oil.

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

A shaft collar portion 6d which is a large diameter portion is provided at the upper portion of the shaft, and an eccentric portion including an eccentric shaft 6a having an eccentricity E and a shaft neck 6c having a smaller diameter than the eccentric shaft 6a is provided at the upper portion. Then, an oil supply vertical hole 6b is formed which penetrates in the axial direction from the lower end portion of the crankshaft 6 through the entire area including the upper eccentric portion. Then, the fueling piece 6x is press-fitted to the lower end portion of the fueling vertical hole 6b, and the fueling upper main horizontal hole 6e, the fueling lower main horizontal hole 6f and the fueling auxiliary horizontal hole 6g are provided in the lateral direction. When the crankshaft 6 is incorporated into the RC compressor, these oil supply lateral holes are installed at positions facing the bearings. The eccentric shaft 6a is inserted into the turning bearing 23 of the turning piston 3 when the crankshaft 6 is incorporated into the RC compressor. Further, the shaft balance 81 described above is press-fit into the shaft collar 6d in the direction opposite to the eccentric shaft 6a.

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

As described above, the crankshaft 6 rotatably supported by the main bearing 24 of the frame 4 is positioned in the axial direction by placing the shaft collar 6 d on the shaft thrust surface 4 c. Then, after the eccentric shaft 1a is made to protrude into the cylinder groove 1c by inserting the eccentric shaft 6a into the eccentric shaft insertion hole 1d of the rolling cylinder 1, the turning piston 3 is inserted to insert the eccentric shaft 6a into the turning bearing 23. Incorporate into the crankshaft 6 As a result, the orbiting piston 3 can rotate on the central axis of the eccentric shaft 1a. That is, the central axis of the eccentric shaft 1 a coincides with the piston rotation shaft 88 which is the rotation shaft of the swing piston 3.

A shaft neck 6c having a diameter smaller than that of the eccentric shaft 6a is provided between the eccentric shaft 6a and the shaft collar 6d so as to pass through the eccentric shaft insertion hole 1d. Further, the orbiting piston 3 has the piston cut surface 3c clearance fitted to the side surface of the cylinder groove 1c, and is incorporated into the rolling cylinder 1 in a slidable manner in the cylinder groove 1c. Thus, the cylinder groove 1 c is divided into two working chambers by the swing piston 3.

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

First, the fixing pin 5 is inserted into the slide groove 3b of the orbiting piston 3, and the slide shaft, which is the central axis of the slide groove 3b, is orthogonal to the pin shaft 61 to constitute a pin slide mechanism. Furthermore, the rolling cylinder 1b of the rolling cylinder 1 is attached to the cylinder hole 2b, and the center line of the cylinder hole 2b and the rolling cylinder shaft 89 are aligned. As a result of combining as described above, the interaxial distance between the shaft axis 87 and the pin axis 61 and the interaxial distance between the shaft axis 87 and the rolling cylinder axis 89 become E, and further, the pin axis 61 centered on the shaft axis 87 And the rolling cylinder axis 89 are disposed at point-symmetrical positions. And, the piston rotation shaft 88 is a circular motion of a turning radius E passing the pin shaft 61 and the rolling cylinder shaft 89 centering on the shaft shaft 87 by the rotation of the crankshaft 6 (this time, clockwise as viewed from above the compressor). I do.

By the way, although mentioned later, the turning piston 3 reciprocates in the cylinder groove 1c. Therefore, it is necessary to extend the length of the orbiting piston 3 so that the eccentric shaft insertion hole 1d is concealed by the orbiting piston 3 even when the orbiting piston 3 is close to the end of the cylinder groove 1c. As the length of the orbiting piston 3 increases, it becomes necessary to extend the length of the cylinder groove 1c, and the diameter of the rolling cylinder 1 increases. When the diameter of the rolling cylinder 1 increases, the diameter of the stationary cylinder 2 incorporating it increases, so the diameter of the chamber 8 increases, which causes a problem that the diameter of the RC compressor increases. As shown in FIG. 1, a shaft neck 6c is provided so as to pass the eccentric shaft insertion hole 1d with a shaft neck 6c whose diameter is smaller than that of the eccentric shaft 6a. As a result, since the eccentric shaft insertion hole 1d can be made smaller, it is possible to suppress the increase in diameter of the RC compressor.

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

In the middle of the compression operation, two working chambers are formed respectively adjacent to the two piston cylindrical peripheral surfaces 3e of the orbiting piston 3. In FIGS. The working chamber is at a maximum volume. That is, the working chamber having a volume 0 is the discharge chamber 105 completing the discharge stroke or the suction chamber 95 starting the suction stroke, and the working chamber having the largest volume is the suction chamber 95 or compression stroke completing the suction stroke To start the compression chamber 100. As will be described later, the rotational direction of the crankshaft 6 and the rotational direction of the rolling cylinder 1 are the same. In the figure, since the crankshaft 6 rotates clockwise, the rolling cylinder 1 also rotates clockwise (arrows indicating the rotational direction of the rolling cylinder 1 are shown in FIGS. 2 and 3). Thus, when the rolling cylinder 1 rotates clockwise, the working chamber with a volume 0 (left working chamber of the orbiting piston 3) in FIGS. 2 and 3 is provided with the suction flow path 2s to start the suction stroke.

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. In addition, when the rolling cylinder 1 rotates slightly counterclockwise (when going back slightly to the time in FIGS. 2 and 3), the working chamber having the largest volume in FIGS. The suction flow path 2s is provided on the Specifically, as shown in FIGS. 2 and 3, the suction groove 2s2 at the bottom of the cylinder hole 2b connected to the suction hole 2s1 continues to communicate with the working chamber (right working chamber of the swing piston 3) which is the suction chamber 95. It is a stretched configuration (see the two-dot chain line in FIG. 3). Although suction hole 2s1 was provided in the vertical direction this time, it may be provided not only in that but in the horizontal direction. In this case, since the suction hole 2s1 and the chamber 8 are close to each other, the suction pipe 50 in the RC compressor can be shortened, so that suction superheat can be suppressed and the performance can be enhanced.

Furthermore, when the rolling cylinder 1 rotates clockwise, the working chamber having the largest volume in FIGS. 2 and 3 starts a sealed state in which neither the discharge passage 2 d nor the suction passage 2 s is communicated to continue the compression stroke. The closed state continues until the compression chamber 100 is reduced to the specific 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 the discharge stroke is started. The discharge flow channel 2d in FIGS. 2 and 3 shows 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 ÷ 2.2 of the suction chamber 95 at the completion of the suction stroke, the cylinder internal discharge groove 2d1 constituting the discharge flow passage 2d together with the cylinder through discharge hole 2d2 and the cylinder external discharge groove 2d3 Is provided at a position where communication with the compression chamber 100 starts. Then, from that time, the compression chamber 100 becomes the discharge chamber 105, and the cylinder internal discharge groove 2d1 is provided to communicate with the discharge chamber 105 in the entire period of the discharge stroke. In addition, although the case where intrinsic volume ratio is 2.2 was shown here, intrinsic volume ratio is not limited to this numerical value, The function of a compression and discharge should just be obtained as a compressor.

Finally, at the time of completion of the discharge stroke where the volume of the discharge chamber 105 is 0 (see the working chamber of volume 0 in FIGS. 2 and 3), the cylinder internal discharge groove 2d1 is positioned and sized so as to be separated from the discharge chamber 105. Provided. In this case, although the discharge portion directly communicating with the discharge chamber 105 is the cylinder internal discharge groove 2d1 provided on the cylindrical peripheral surface of the cylinder hole 2b, the present invention is not limited thereto. The groove provided at the bottom of the cylinder hole 2b such as the suction groove 2s2 It may be In this case, the discharge flow path 2d can be set even when the specific volume ratio is large and compression must be performed to reduce the volume of the compression chamber 100 at the start of the discharge stroke.

Having described the configuration of the compression unit, the operation of the compression unit will be described next using FIGS. 9, 10 and 11 (all of which are sections slightly lower than the section BB in FIG. 1). Here, since the suction groove 2s2 is in front of the cross section BB in FIG. 1, it should originally be represented by an imaginary line by a two-dot chain line. However, since a two-dot chain line in a small figure is difficult to distinguish as a 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 having the pin slide mechanism as the rotation halving mechanism is the pump operation which can be regarded as identical except that the time difference between the suction stroke end and the discharge stroke start is set extremely small. As such, only a brief description is given herein. Moreover, the overcompression suppression means which is not described in patent document 1 is also demonstrated.

FIG. 9 shows the state of the compression element every 45 degrees while the crankshaft 6 makes one rotation clockwise about the shaft axis 87 (the intersection of the center lines of the respective drawings). The entire stroke (suction stroke, compression stroke, discharge stroke) of the compression operation is completed by rotating the crankshaft 6 twice. For this reason, FIG. 9 shows only half of the stroke, but utilizing the fact that two working chambers make a change by one rotation offset in crank angle in parallel, the second rotation stroke of the other working chamber Explain using change. The description explains the travel of the working chamber to the left of the pivoting piston 3 in the top left view of FIG. Then, the crank angle at this time is set to 0 degrees.

In the upper left view (see the enlarged view of FIG. 10) of FIG. 9 where the crank angle is 0 degrees, the piston rotation shaft 88 overlaps the pin shaft 61. And, the volume is zero. This is a transition time when the immediately preceding discharge stroke is finished and the suction stroke is started. If the volume can be made strictly zero, there is no big problem even if both flow paths and this working chamber are in communication. However, when the piston cylindrical peripheral surface 3e collides with the inner peripheral surface of the cylinder hole 2b, the reliability is impaired, and problems such as an increase in noise and vibration and a decrease in efficiency due to an increase in sliding loss at the collision point occur.

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

Therefore, in the actual setting, the

flow paths

2s and 2d are not communicated. However, since the period in which both flow

paths

2s and 2d are not communicated to the working chamber is extremely short, it is not clearly shown in FIGS.

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

Here, when the crank angle is 180 degrees, the piston rotation shaft 88 and the rolling cylinder shaft 89 coincide with each other. For this reason, the rolling cylinder 1 achieves meshing even if it causes an irregular rotation different from the regular rotation that follows the half of the pivoting amount of the pivoting piston 3.

In actuality, the above-mentioned irregular rotation of the rolling cylinder 1 frequently occurs due to the deviation from the ideal rotation coming from the gap between the rolling cylinder 1, the swing piston 3 and the stationary cylinder 2. Once this non-normal rotation occurs, as pointed out in Patent Document 1, it is impossible to automatically return to normal rotation dynamically, and the compression operation is stopped. In order to continuously avoid such a locked state and continue the smooth compression operation, in the present embodiment, the rotation synchronization means for synchronizing the rotation of the rolling cylinder 1 and the rotation of the rotation piston 3 is provided and then the rotation is performed. The rotation half means is provided to reduce the amount of rotation of the piston 3 to half of the amount of rotation.

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 realized by gap fitting the piston cut surface 3c of the orbiting piston 3 to the side surface of the cylinder groove 1c. The rotation amount of the rolling cylinder 1 synchronized with the rotation of the orbiting piston 3 can be defined to be half of the orbiting amount of the orbiting piston 3 by combining the half rotation means. That is, the rotation of the rolling cylinder 1 can always be defined as normal rotation.

As described in Patent Document 1, the rotation half means of the orbiting piston 3 inserts the fixing pin 5 fixed to the stationary cylinder 2 in the slide groove 3b provided on the piston top surface 3d which is the top surface of the orbiting piston 3. This is realized by the pin slide mechanism that is configured. The prescribed degree (regularity) that defines the rotation amount of the orbiting piston 3 by this pin slide mechanism as half of the orbiting amount changes with the crank angle. As described in Patent Document 1, while the crank angle is maximized at 180 degrees, when the crank angle is 0 degree (see FIG. 11 of Patent Document 1), the pin shaft 61 and the piston rotation shaft 88 coincide with each other. Since the rotation amount of the orbiting piston 3 is not defined by the pin slide mechanism, it can be understood that the prescribed degree is minimized. However, when the crank angle is 0 degree, the piston rotation shaft 88 and the rolling cylinder shaft 89 are farthest apart, so originally there was no problem in the compression operation and the pin slide mechanism was unnecessary.

From the above, the regularity of the pin slide mechanism shows an ideal change in which the increasing necessity of the crank angle increases near 180 degrees and decreases near the decreasing crank angle of 0 degrees. As a result, it is not necessary to improve the dimensional tolerance and the assembly accuracy of the compression elements that constitute the compression mechanism, and it is possible to reduce the manufacturing cost.

This also shows that the pin slide mechanism has a high frequency of defining the movement of the compression element at a crank angle near 180 degrees. That is, the crank angle is concentrated around 180 degrees, and a load is applied to the fixed pin 5 and the slide groove 3b, which are pin mechanisms, and the size of the load is ideal for difficult-to-predict compression elements generated from the gaps between the parts. Due to deviations from movement, with irregular and shocking changes.

As mentioned above, since an irregular and impulsive load is applied to a pin slide mechanism, it becomes essential to perform reliable lubrication. By the way, since the load applied to the slide groove 3b acts from the fixing pin 5, the pin slide mechanism may be lubricated by supplying oil to the pin mechanism. Therefore, in the RC compressor which realizes smooth compression operation by means of the rotation synchronization means and the rotation half means by the pin slide mechanism, oil supply to the pin mechanism is essential. The description of the pin oiling mechanism will be made in the description of the flow of oil described later.

By the way, the method of making the piston cut surface 3c of the orbiting piston 3 as the rotation synchronizing means clearance fit to the side surface of the cylinder groove 1c functions as a seal between working chambers separated by the orbiting piston 3 and having a pressure difference. doing. For this reason, the sealability is significantly improved as compared with the wire seal as in Patent Document 2, and the compressor efficiency is improved.

The stroke after the second rotation is described in the other working chamber of FIG. 9 (right working chamber in the upper right figure) as described above. In the working chamber which has been the suction chamber 95 up to this point, the suction flow path 2s is separated and becomes a sealed space. As a result, the compression stroke is started, and the working fluid in the working chamber is reduced in volume and compressed. That is, the working chamber is the compression chamber 100. This compression stroke is completed by communication between the compression chamber 100 and the discharge flow passage 2d before the volume of the compression chamber 100 approaches 0 in the lower left view of FIG. The working fluid thus obtained is discharged into the machine of the RC compressor through the discharge flow path 2d.

For example, when the compression chamber volume at the time of discharge is 1 / 2.2 of the volume of the suction chamber 95 at the completion of the suction stroke, that is, the specific volume ratio is 2.2, the transition from the compression stroke completion to the discharge stroke open The timing is shown enlarged in FIG. This discharge stroke continues until the crank angle shown in FIG. 9 is 360 degrees, that is, 0 crank angle. Further, a bypass hole 2e always faces the compression chamber 100 during the compression stroke. As a result, at the time of over-compression, the bypass hole 2e and the bypass valve 22 of the one-way valve provided on the upper side perform the operation of flowing the working fluid in the compression chamber 100 into the machine space of the chamber 8 which is the discharge pressure. That is, the over-compression suppression means is configured. As a result, during the over-compression operation, extra compression can be avoided, so that 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 is shifted to the discharge chamber 105. This can be understood from the fact that the bypass hole 2e faces the discharge chamber 105 in the drawing of FIG. From this, the bypass hole 2e at this point of time plays a role of the discharge flow path. Therefore, the discharge flow path resistance can be reduced, and the compressor efficiency can be improved.

Furthermore, it can be seen that the bypass hole 2e is also exposed to the working chamber when the suction chamber 95 is in operation. 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 completing the suction stroke in the drawing of 0 crank angle in 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 undergoing fluid compression can be discharged from the compression chamber 100 at the bypass hole 2e, so an excessive pressure rise It is possible to avoid damage to the compression section due to the effect of improving the reliability.

In the present embodiment, a flapper type valve is used as the bypass valve. As a result, 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. Here, the bypass valve may of course be a reed valve type. In this case, since the structure is simple, there is an effect of cost reduction.

Next, the flow of oil in the compression section will be described with reference to FIGS. 9 and 12 (an enlarged view of a portion M in FIG. 3 in the BB section of FIG. 1) and FIG. Here, oil supply to the pivot bearing 23 and the main bearing 24, oil supply passages to the pin mechanism which is a feature of the present invention, and differential pressure oil supply for flowing oil to the oil supply passages will be described. Then, a back pressure supporting means will be described which uses the back pressure used in differential pressure refueling to avoid the problem of the gap expansion caused by the refueling of the pin mechanism. Furthermore, a description will be given of refueling of the compression chamber by the back pressure flow path for setting the back pressure.

As described above, the oil supply passage connecting the oil storage portion 125 to the main bearing 24 is provided by the oil supply pipe 6x constantly immersed in the oil storage portion 125, the oil supply vertical hole 6b, the oil lower main lateral hole 6f, and the oil upper main lateral hole 6e. Furthermore, since the vertical feed hole 6b is a hole that also penetrates the eccentric shaft 6a at the upper end of the crankshaft 6, the feed path leading to the pivot bearing 23 press-fit to the pivot piston 3 and the slide of the pivot piston 3 An oil supply passage connected to the fixing pin 5 which is a pin mechanism is formed through the groove 3b.

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

However, since a narrow gap is set between these areas and the fixing pin 5 (the gap between the piston upper surface 3 d and the bottom of the cylinder hole 2 b), fluid such as working fluid can not flow into the fixing pin 5 from these gaps. . As a result, there is a high possibility that the fixed pin 5 can be refueled by the pin oil supply passage whose flow path resistance to the fixed pin 5 is substantially zero. Here, the gap between the piston upper surface 3 d and the bottom surface of the cylinder hole 2 b depends on the height of the bottom surface of the cylinder groove 1 c in which the orbiting piston 3 is installed. That is, it depends on the built-in height of the rolling cylinder 1.

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

By the way, in order to flow oil to the oil supply passage, a means for applying a driving force to the oil is required. In this example, the discharge pressure is equal to or less than the discharge pressure in a space (hereinafter referred to as a back pressure chamber 110) formed between the lower end of the orbiting bearing 23 and the upper end of the main bearing 24, ie, below the orbiting piston 3 and the rolling cylinder 1. Apply a pressure (hereinafter referred to as a back pressure, which naturally becomes equal to or higher than the suction pressure). This is because the space is a space upstream of each oil supply passage, and differential pressure oiling is realized by making the pressure lower than the oil storage portion 125 of the discharge pressure which is the space downstream. As a result, oil is supplied not only to the main bearing 24 but also to the orbiting bearing 23, which has the effect of improving the reliability of both bearings.

Further, oil is also supplied abundantly to the upper part of the eccentric shaft 6a in the middle of the oil supply path to the turning bearing 23. Therefore, since the flow resistance of the pin oil supply passage to the fixing pin 5 at the upper part of the eccentric shaft 6a is substantially zero as described above, the discharge pressure oil is abundantly supplied to the fixing pin 5. As a result, reliable oil supply to the pin mechanism, which is a problem of the pin slide mechanism, can be realized, and the reliability of the RC compressor can be improved.

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

By the way, the direction of relative movement of the fixing pin 5 in the slide groove 3b is always directed to the side for setting the discharge flow path 2d in which the suction flow path 2s is not set (moves downward in each drawing of FIG. 9) . From this, a configuration is conceivable in which the upper space of the eccentric shaft 6a is narrowed in order to intentionally generate oil compression in the slide groove 3b. In this case, the pressure of the oil becomes a pressure higher than the discharge pressure, and the oil can be supplied to the discharge pressure area in the vicinity of the discharge flow path 2d. Therefore, the leakage of the working fluid from the discharge pressure area can be suppressed. It becomes. This has the effect of improving the compressor efficiency.

This concludes the description of the refueling to each part by differential pressure refueling, and next, the harmful effects that occur in the installation of the pin refueling passage and the measures therefor will be described.

Since the oil of the discharge pressure can be poured into the pin mechanism abundantly by the pin oil supply passage, the reliability of the fixed pin 5 is improved. As a result, the discharge pressure and the pressure in the vicinity of the piston upper surface 3d of the orbiting piston 3 Become. Further, the area of the discharge pressure also spreads on the upper surface of the rolling cylinder 1b which is the upper surface of the rolling cylinder 1 adjacent to the piston upper surface 3d. Thereby, the swing piston 3 and the rolling cylinder 1 try to move downward. When this movement occurs, the gap between the upper surface 3 d of the piston and the upper surface of the rolling cylinder 1 b and the bottom surface of the cylinder hole 2 b (hereinafter referred to as “upper gap”) is enlarged. In this case, the working fluid leaks from the discharge chamber 105 or the high pressure compression chamber 100 close to the discharge pressure to the low pressure components through the upper clearance. It also leaks to the suction chamber 95, which is a low pressure space, causing an internal leak and reducing the compressor efficiency.

Furthermore, since the working fluid flows into the above-described pin mechanism, pin lubrication becomes uncertain, and in the worst case, lubrication can not be performed. Then, the oil supply to the orbiting bearing 23 becomes unreliable, and the reliability of the fixed pin 5 and the orbiting bearing 23 which are pin mechanisms is impaired. From the above, it is essential to take measures not to enlarge the upper clearance even if the pin mechanism is refueled.

In this example, while adjusting the clearances of each part so that the amount of oil supply by differential pressure oiling can ensure necessary oiling, the back pressure which is the pressure of the back pressure chamber 110 is raised, and the rolling cylinder 1 and the orbiting piston 3 are A back pressure support means which always biases the stationary cylinder is used (the method of setting the back pressure will be described later). Thus, the expansion of the upper gap can be avoided, so that the fixing pin 5 which is the pin mechanism, the turning bearing 23 and the main bearing 24 can be reliably supplied with oil, and the reliability of the RC compressor can be improved. Since it is possible to suppress internal leaks in which the leakage flow path is established, the compressor efficiency of the RC compressor can be improved.

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

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

As apparent from FIG. 9, the compression chamber 100 of the RC compressor moves relative to the stationary cylinder 2 by the rotation of the rolling cylinder 1 and the movement of the orbiting piston 3 to the outer peripheral side. Therefore, by providing the back pressure introduction port of the back pressure direct current passage 200 in the stationary cylinder 2, it becomes possible to introduce a desired pressure into the back pressure chamber 110. In practice, the back pressure DC path 200 is connected so as to connect to the compression chamber 100 in a range in which the volume ratio (maximum volume of suction chamber / compression chamber volume) becomes a desired back pressure value as the average value. Provide a back pressure inlet.

By setting the back pressure direct current passage 200 as described above, the back pressure becomes higher than the pressure of the compression chamber 100 immediately after the back pressure direct current passage 200 starts conduction with the compression chamber 100. Thus, the oil flowing into the back pressure chamber 100 can be discharged to the compression chamber side. As a result, it is possible to continue the refueling to each part, continuously maintain the reliability of each part to be refueled and the sealability by the refueling, and it is possible to operate the compressor stably.

In this example, the back pressure direct current passage 200 is set at a position not facing the suction chamber 95, but in some cases, it may be a position facing the suction chamber 95 at the initial communication stage of the back pressure direct current passage 200. In this case, since the suction chamber 95 can be refueled by the back pressure direct current passage 200, the compressor efficiency can be improved by the improvement of the volume efficiency. However, if the oil temperature is high, suction heating may be large, and the volume efficiency may be reduced. Therefore, it is necessary to adjust the communication section of the back pressure DC path 200 according to the operating conditions.

As described above, the oil that has flowed into the compression chamber 100 by the back pressure direct current passage 200 improves the sealability of the compression chamber 100. Therefore, the internal leakage of the compression stroke can be suppressed, and the compression efficiency can be improved. Thus, the oil that has flowed into the compression chamber 100 finally shifts to the discharge stroke together with the working fluid, and is discharged to the inside of the compressor through the discharge flow path 2d as described above.

In this embodiment, at the lower end opposite to the cylinder groove 1c of the rolling cylinder 1, a flat rolling end plate 1a perpendicular to the rolling cylinder shaft 89 is provided as a rolling end. This is because the end plate front surface which is the upper surface of the rolling end plate 1a is biased to the cylinder mounting surface 2a by the biasing of the rolling cylinder 1 toward the stationary cylinder 2 side by the back pressure support described above. As a result, the sealability between the back pressure chamber 110 and the suction chamber 95, the compression chamber 100, and the discharge chamber 105 is improved, and the effect of suppressing the internal leak and improving the compressor efficiency can be obtained. However, the sealability is not perfect and some leaks occur. In that case, the oil flowing into the back pressure chamber 110 flows to the suction chamber 95 or the compression chamber 100 whose pressure is lower than the back pressure. This improves the sealability. Further, the oil that has flowed into the suction chamber 95 has the effect of improving the compressor efficiency by improving the volumetric efficiency, since the sealability of the suction chamber 95 is improved.

Furthermore, in the present embodiment, since the discontinuous familiar film 85 is provided on the surface of the orbiting piston 3 or the rolling cylinder 1, the upper clearance or the end plate front surface (upper surface of the rolling end plate 1a) and the cylinder mounting surface 2a and between the lower surface 3f of the piston and the bottom surface of the cylinder groove 1c are reduced as a whole along with the shape correction to reduce the leakage loss and to make the shapes thereof smooth to reduce the sliding loss. And the compressor efficiency is improved. In addition, even on the opposite surface (for example, between the outer peripheral surface of rolling cylinder 1b and the inner peripheral surface of cylinder hole 2b or between piston cut surface 3c and the side surface of cylinder groove 1c) which is not biased by back pressure support After that, the gap is reduced as compared with the case where the familiar film is not provided, so that the sealing performance is improved, and the compressor efficiency is improved.

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

Also in this case, the rolling cylinder 1 and the annular end plate can be separate parts. Then, the machining of the cylinder groove 1c of the rolling cylinder 1 and the machining of the rolling end plate 1a can be respectively performed by a lathe, and there is also an effect that the machining cost is reduced. Of course, the rolling cylinder 1 and the rolling end plate 1a may be joined by welding, screwing or the like.

Next, an RC compressor according to a second embodiment will be described with reference to FIG. FIG. 15 is an enlarged cross-sectional view near the surface of the rolling cylinder 1 or the orbiting piston 3 and is a continuous familiar film 86 except that the compatibility decreases continuously as it goes inward from the surface. Since the same as in the case of FIG. Preferably, the continuous familiar film 86 is also formed over the entire sliding surface.

An example of such a film is a surface-modified familiar film which is dipped in a treatment agent to modify the surface. As shown in FIG. 15, the composition is deposited on the surface of the original base material onto the surface to react with the treatment agent to form a highly compatible deposited layer, and the original base material side is eroded and porous. It can be realized by forming an eroded layer which is slightly conformable to the base material but slightly conformable to the place of the base material, but less conformable than the deposit. For example, when the base material is cast iron, there is a coating formed by manganese phosphate treatment. As a result, peeling of the coating is less likely to occur than in the case of the discontinuous familiar coating 85, and the reliability is improved.

In addition, since a certain degree of familiarity occurs even at the original surface position of the base material, it becomes easy to control the base material dimension to which the familiar film is provided. For example, even if the height of the orbiting piston 3 in the base material is slightly larger than the depth of the cylinder groove 1c in the base material, the continuous familiar film 86 of the orbiting piston 3 can cause wear to less than the base material size. That is, since the tolerances of the base material dimensions can be set to allow mutual interference, the distance between the dense surfaces (between the base surfaces of the base material) when unmatched becomes smaller, and the sealability is further improved and the compression is achieved. There is an effect that the machine efficiency is improved.

Next, an RC compressor according to a third embodiment will be described using FIGS. 16 and 17. FIG. 16 is an enlarged cross-sectional view of part M of FIG. FIG. 17 is a vertical cross-sectional view taken along the line O-G in FIG. 16 and shows a cross section of a portion where a back pressure valve channel is installed. The second embodiment is the same as the first or second embodiment except that the back pressure valve channel 210 is used as the back pressure setting method for the back pressure supporting means, and therefore the description of the same portions will be omitted.

Similar to the back pressure direct current path 200 of the first embodiment, the back pressure valve flow path 210 is configured as a U-shaped flow path. However, since the compression chamber 100 in communication has a pressure increase due to the back pressure valve 26 described later, the compression chamber 100 is in communication with the compression chamber 100 on the lower pressure side than in the back pressure chamber DC path. Therefore, the position of the vertical hole on the compression chamber 100 side is changed to be the vertical hole 2h4 for the compression chamber side back pressure valve. Furthermore, since the back pressure valve 26 described later bears the setting of the pressure difference, the diameter of each hole is increased.

Here, in the case of the

embodiment

1 or 2 in which the slide groove 3b is connected to the piston cut surface 3c, the compression chamber side back pressure valve vertical hole 2h4 is in the slide groove 3b between the crank angle 225 degrees and the crank angle 270 degrees in FIG. I will come. Since the slide groove 3b is filled with the oil of the discharge pressure and the working fluid of the discharge pressure generated therefrom, the discharge pressure is applied to the space for the compression chamber side back pressure valve vertical hole 2h4 and the back pressure valve flow path 210 connected thereto. Fluid flows in. When the compression chamber side back pressure valve vertical hole 2h4 reaches the compression chamber 100, the fluid flows into the compression chamber 100 having a pressure lower than the discharge pressure to cause an internal leak, so the performance is lowered. Therefore, in the present embodiment, slide groove both-ends sealing portions 3b1 shown by cross hatching in FIG. 16 are provided to avoid the internal leak described above and to suppress the performance deterioration.

Thereby, since the drill bit used for processing can be changed into a thick thing, the risk of damage reduces, and there is an effect that processing becomes easy and processing cost reduces. In addition to the U-shaped flow path configured as described above, in this example, the back pressure valve hole 2 h 5 is processed from the upper surface side of the stationary cylinder 2, and the back pressure valve 26 is installed therein. Therefore, the back pressure valve flow path 210 is configured to include the compression chamber side back pressure valve vertical hole 2 h 4, the back pressure horizontal hole 2 h 2, the back pressure chamber side back pressure vertical hole 2 h 3, the back pressure valve hole 2 h 5 and the back pressure valve 26. The back pressure chamber side back pressure vertical hole 2h3 communicates with the bed outer peripheral groove 4f and is further connected to the back pressure chamber 110 through the bed radial groove 4e.

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

First, the back pressure valve piece 26 a is press-fitted and fixed to the bottom of the back pressure valve hole 2 h 5. Then, the back pressure valve plate 26b is placed thereon, the back pressure valve spring 26c is disposed thereon, and the back pressure valve hole 2h5 is sealed by the back pressure valve cap 26d. At this time, the back pressure valve spring 26c is compressed to press the back pressure valve plate 26b against the back pressure valve piece 26a with a predetermined force.

The back pressure valve 26 is opened when the back pressure is higher than the average pressure of the compression chamber 100 by which the back pressure is communicated by a fixed value corresponding to the pressing force of the back pressure valve spring 26c against the back pressure valve piece 26a. Control the pressure.

Here, the oil flowing into the above-described back pressure chamber 110 is used as a fluid for increasing the pressure in the back pressure chamber 110. That is, the back pressure chamber fluid introduction path is all the inflow paths of the oil flowing into the back pressure chamber 110. Specifically, it is a flow path which flows in from the main bearing 24 and a flow path which flows in from the turning bearing 23.

As described above, due to the back pressure setting by the back pressure valve channel, the back pressure value becomes a pressure that is approximately a fixed value higher than the pressure of the compression chamber in communication. This is because the pressure close to the minimum pressure required to urge the orbiting piston 3 and the rolling cylinder 1 to the stationary cylinder 2 is a value close to the pressure required when the over-compression suppressing means using the bypass valve 22 etc. described above is adopted. The sliding loss generated with the biasing can be reduced. Therefore, there is an effect that the compressor efficiency can be improved.

Next, an RC compressor according to a fourth embodiment will be described with reference to FIG. FIG. 18 is an enlarged vertical sectional view of a portion P in FIG. In this figure, in order to fix the fixing pin 5 which is the simplest pin mechanism, a pin fixing flange 5 a is provided and screwed with a pin fixing screw 91. The other parts are the same as in the first to third embodiments, and therefore the description of the same parts will be omitted.

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

In the present embodiment, by providing the pin fixing flange 5a, an impact load can be received on the surface of the pin fixing flange 5a. In addition, since the fixing pin 5 can be fixed by the pin fixing screw 91, it is possible to prevent the fixing pin 5 from falling off, and there is an effect that the reliability of the compressor is improved. By the way, although only one pin fixing screw 91 is shown in FIG.

Next, an RC compressor according to a fifth embodiment will be described with reference to FIGS. 19 and 20. FIG.

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

In these figures, a slider 5c rotatable with respect to the pin axis is provided, thereby providing a pin mechanism. The other parts are the same as in the first to fourth embodiments, and therefore the description of the same parts will be omitted.

In this embodiment, as shown in FIG. 19, in the pin mechanism, the slider 5c rotatable relative to the pin axis is installed on the lower surface of the fixing pin 5 by the slider holding flange 5b. The slider 5c is an element which is fitted in the slide groove 3b with a gap. As shown in FIG. 20, the slider 5c has a slider center hole 5c2 and a slider cut surface 5c1. The slider cut surface 5c1 is provided as two flat portions parallel to each other, and is a portion to be fitted with a gap in the slide groove 3b.

After inserting the slider holding flange 5b into the slider center hole 5c2 with a small amount of slack (play), the pin mechanism is manufactured by press-fitting to the fixing pin 5.

Thereby, an impact load applied to the pin mechanism is applied from the side surface of the slide groove 3b to the slider cut surface 5c1, and further applied from the slider center hole 5c2 to the axis of the slider holding flange 5b. Since the former is flat planes and the latter is cylindrical peripheral surfaces, the delivery of loads at two locations does not involve delivery of loads with concentrated loads. For this reason, concentration of load in the pin mechanism can be suppressed, and there is an effect that the reliability is improved.

Next, an RC compressor according to a sixth embodiment will be described using FIGS. 21 and 22. FIG. FIG. 21 is an enlarged vertical cross-sectional view of a portion Q in FIG. 1, and FIG. 22 is a perspective view showing a modified example of the rolling cylinder 1.

In these figures, the rolling end plate 1a which is a collar of the rolling cylinder 1 of FIG. 4 is replaced with a cylindrical rolling cylindrical end 1h. The other parts are the same as in the first to fifth embodiments, and therefore the description of the same parts will be omitted.

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

1: Rolling cylinder, 1a: rolling end plate, 1b: rolling cylinder, 1c: cylinder groove, 1d: eccentric shaft insertion hole, 1h: rolling cylinder end, 2: stationary cylinder, 2a: cylinder mounting surface, 2b: cylinder hole , 2d: discharge flow channel, 2d1: cylinder internal discharge groove, 2d2: cylinder penetrating discharge hole, 2d3: cylinder external discharge groove, 2e: bypass hole, 2h1: compression chamber side back pressure vertical hole, 2h2: back pressure horizontal hole, 2h3: Back pressure chamber side back pressure vertical hole, 2h 4: vertical hole for compression chamber side back pressure valve, 2h 5: back pressure valve hole, 2s: suction passage, 2s 1: suction hole, 2s 2: suction groove, 3: swirl piston, 3a: swirl bearing hole , 3b: slide groove, 3c: piston cut surface, 4: frame, 4d: bed surface, 5: fixing pin, 5a: pin fixing flange, 5b: slider holding flange, 5c: slide Da, 5c1: Slider cut surface, 6: Crankshaft, 6a: Eccentric shaft, 6b: Refueling vertical hole, 6c: Shaft neck, 6d: Shaft collar, 7: Motor, 7a: Rotor, 7b: Stator, 8: Chamber, 8a: chamber cylindrical portion, 8b: chamber upper lid, 8c: chamber lower lid, 22: bypass valve, 23: pivot bearing, 24: main bearing, 25: auxiliary bearing, 26: back pressure valve, 26a: back pressure valve piece, 26b A: back pressure valve plate, 26 c: back pressure valve spring, 26 d: back pressure valve cap, 35: lower frame, 50: suction pipe, 55: discharge pipe, 85: discontinuous compatible film, 86: continuous compatible film, 90: cylinder Bolt, 95: suction chamber, 100: compression chamber, 105: discharge chamber, 110: back pressure chamber, 125: oil reservoir, 200: back pressure DC path, 210: back pressure valve path, 220 Hermetic terminal.

Claims

A crankshaft having an eccentric shaft centered on the shaft axis,
A frame pivotally supporting the crankshaft;
A rotational drive source for applying a rotational drive torque to the crankshaft;
A compression unit for suctioning, compressing and discharging working fluid;
And an oil storage unit,
The compression unit includes a rolling cylinder having a cylinder groove, a swing piston slidably housed in the cylinder groove, and a stationary cylinder having an eccentric cylinder hole rotatably accommodating the rolling cylinder.
A space surrounded by the rolling cylinder, the orbiting piston, and the stationary cylinder functions as a suction chamber, a compression chamber, and a discharge chamber as the rolling cylinder and the orbiting piston rotate.
The eccentric shaft has a center line different from the shaft axis,
The orbiting piston is disposed rotatably around the center line of the eccentric shaft, and revolves according to the rotation of the crankshaft.
The eccentric cylinder hole of the stationary cylinder is additionally provided with a fixing pin having a center line different from the shaft axis,
The pivot piston has a slide groove, and the fixing pin has a configuration slidably fitted in the slide groove,
The middle point of the line connecting the intersection of the bottom of the eccentric cylinder hole with the center line of the fixing pin and the intersection of the bottom of the eccentric cylinder hole and the center line of the rolling cylinder is the eccentric cylinder hole At the intersection of the bottom surface and the centerline of the shaft axis, the three centerlines are arranged parallel to each other, whereby the rotation of the orbiting piston and the rotation of the rolling cylinder are synchronized. And adjusting the rotational angular velocity of the orbiting piston to half the rotational angular velocity of the crankshaft,
The lubricating oil of the oil storage portion is fixed to the fixing pin and the oil by forming an oil communication passage connecting the oil storage portion and the slide groove so that the pressure of the oil storage portion is equal to the pressure of the discharge chamber. Rolling cylinder positive displacement compressor that supplies slide grooves.
The rolling cylinder positive displacement compressor according to claim 1, wherein the oil communication passage is constituted by an oil supply vertical hole which penetrates the crankshaft and the eccentric shaft and communicates with the slide groove.
The pivoting piston has two piston cutting surfaces which are parallel and flat to one another;
The cylinder groove has two inner side portions parallel and flat to one another,
The rolling cylinder positive displacement compressor according to claim 1 or 2, further comprising a configuration in which the two piston cut surfaces are slidably fitted between the two inner side surfaces.
A back pressure chamber is provided between the rolling cylinder and the frame;
The stationary cylinder has a back pressure DC path communicating the compression chamber with the back pressure chamber, and the pressure in the back pressure chamber is an intermediate pressure between the pressure in the suction chamber and the pressure in the discharge chamber. The rolling cylinder positive displacement compressor according to any one of claims 1 to 3, which is configured as follows.
The rolling cylinder positive displacement compressor according to claim 4, wherein a back pressure valve is attached to a flow passage communicating the compression chamber and the back pressure chamber.
The rolling cylinder positive displacement compressor according to any one of claims 1 to 5, wherein the number of the compression part is one.
The rolling cylinder positive displacement compressor according to claim 6, wherein the compression unit, the rotational drive source, and the oil storage unit are arranged in this order and connected by the crankshaft.
The rolling cylinder has an eccentric shaft insertion hole,
The rolling cylinder positive displacement compressor according to any one of claims 1 to 7, wherein the turning piston is configured to close the eccentric shaft insertion hole.
9. The rolling piston positive displacement compressor according to claim 8, wherein a shaft neck having a diameter smaller than that of the eccentric shaft is provided between the eccentric shaft and the rotation shaft of the crankshaft.
The rolling cylinder positive displacement compressor according to any one of claims 1 to 9, wherein a bypass hole having a bypass valve which is a one-way valve is provided at the bottom of the eccentric cylinder hole.
The rolling cylinder includes a rolling cylinder having the cylinder groove and a rolling end plate,
The rolling cylinder positive displacement compressor according to any one of claims 1 to 10, wherein a diameter of the rolling end plate is larger than a diameter of the rolling cylinder.
The rolling cylinder is a rolling cylinder having the cylinder groove, and has a configuration in which a rolling end plate separate from the rolling cylinder is stacked on the rolling cylinder.
The rolling cylinder positive displacement compressor according to any one of claims 1 to 10, wherein a diameter of the rolling end plate is larger than a diameter of the rolling cylinder.
The rolling cylinder type according to any one of claims 1 to 12, wherein a step is provided between a bottom portion of the cylinder groove and an end plate front surface which is the cylinder groove side of the rolling end plate. Displacement compressor.
The rolling cylinder positive displacement compression according to any one of claims 1 to 10, wherein the rolling cylinder includes a rolling cylinder having the cylinder groove and a rolling cylinder end having a diameter equal to the rolling cylinder. Machine.
The rolling piston positive displacement compressor according to any one of claims 1 to 14, wherein a compatible film is provided on the surface of at least one of the rolling cylinder and the orbiting piston.