WO1995016136A1

WO1995016136A1 - Swinging rotary compressor

Info

Publication number: WO1995016136A1
Application number: PCT/JP1994/002020
Authority: WO
Inventors: Yasushi Yamamoto
Original assignee: Daikin Industries, Ltd.
Priority date: 1993-12-08
Filing date: 1994-12-01
Publication date: 1995-06-15
Also published as: MY119158A; KR100322269B1; DE69427186T2; CN1117755A; CN1041453C; DE69427186D1; KR960701306A; ES2158069T3; JP3473067B2; DK0683321T3; EP0683321B1; EP0683321A4; JPH07158574A; EP0683321A1; SG43887A1

Abstract

A swinging rotary compressor comprising a cylinder (1) having therein a cylinder chamber (11), a roller (2) fitted in an eccentric shaft portion (31) of a driving shaft (3) and installed in the cylinder chamber (11), a blade (21) provided integrally with the roller (2) in such a manner as to protrude therefrom so as to divide the cylinder chamber (11) into a compression chamber (X) and a suction chamber (Y) and a supporting body (4) disposed in the cylinder (1) so as to freely swing therein and having a receiving groove (41) for receiving retractably the leading end of the blade (21), wherein an oil groove (22) is formed in the blade (21) and the axial end surfaces of a base portion of the roller (2) from which the blade protrudes in such a manner that the groove is open to the inner circumferential surface of the roller (2) at one end and to the protruding leading end of the blade (21) at the other end thereof, wherein a high pressure chamber (15) closed relative to the outside of the cylinder (1) is formed in the receiving groove (41) of the supporting body (4) on the back side of the blade (21), whereby sliding contact portions between the upper and lower end surfaces of the blade (21) and the roller (2), as well as between the blade (21) and the supporting body (4) for supporting the blade are positively lubricated to thereby improve the reliability.

Description

Description Oscillating rotary compressor Technical field

The present invention relates to an oscillating rotary compressor mainly used for a refrigeration system. Background art

Conventionally, as a swing type rotary compressor, for example, as described in Japanese Patent Application Laid-Open No. 5-220874, a blade for partitioning a cylinder chamber into a suction chamber and a compression chamber is provided. The blade is integrally protruded from the roller inserted into the eccentric part of the drive, and the blade is swingably supported in the receiving groove of the support rotatably arranged on the cylinder to expose the roller. There is known an apparatus that compresses a gas fluid. That is, as shown in FIG. 1, the conventional rotary compressor of the conventional type has a radially outward direction in a cylinder chamber A1 of a cylinder A in which a front and a head are contacted on both axial sides. A roller B integrally provided with a protruding blade B 1 is disposed such that both upper and lower end surfaces of the roller B and the blade B 1 are in sliding contact with the fusing surfaces of the respective heads. A cylindrical support C which is slidably contacted with each of the above-mentioned heads is rotatably supported inside the cylinder A, and a receiving groove C1 formed in the support C is provided at a tip end of the blade B1. Oscillates and advances and retreats, thereby partitioning the interior of the cylinder chamber A1 into a compression chamber X and a suction chamber Y via the roller B and the blade B1, while being driven by the roller B. The eccentric part of the shaft is inserted and the roller B is By revolving driven by Da chamber A within 1 sucks the gaseous fluid into the suction chamber Y, also, the pressure The compression of the gas fluid is performed in the contraction chamber X.

In the above compressor, since the upper and lower end surfaces of the roller B and the breaker KB 1 are in sliding contact with the respective heads, lubricating oil is supplied to the upper and lower end surfaces of the roller B and the breaker KB 1. Requires lubrication. Therefore, conventionally, high-pressure lubricating oil supplied to a sliding contact portion between the eccentric portion of the drive shaft and the inner peripheral surface of the roller B is supplied to the inner peripheral side of the roller B and the suction chamber Y. The liner oil is made using the pressure difference between the compression chamber X in the compression process and the pressure difference between the suction chamber Y and the compression chamber X.

That is, not only in the suction chamber Y but also in the compression chamber X, up to the stage before the gas fluid is compressed to a predetermined pressure in the compression chamber X, the pressure between the pressure on the inner circumferential surface side of the roller B and the compression chamber X is higher or lower. A pressure difference is generated, and a height difference pressure is also generated between the suction chamber Y and the compression chamber X. By utilizing these height difference pressures, a pressure difference between the roller 1B and the eccentric portion is obtained. After lubricating the roller B, high-pressure lubricating oil is introduced from the inner peripheral side of the roller B into the compression chamber X and the suction chamber Y via the upper and lower end surfaces of the roller B as indicated by the solid arrow n in FIG. Or, the upper and lower ends of the roller B and the blade B1 are lubricated by being introduced from the compression chamber X to the suction chamber Y via the upper and lower ends of the blade B1.o

However, as described above, the lubrication between the front and rear heads and the upper and lower end surfaces of the roller B and the blade B1 that slides on the face surfaces of the heads, as described above, requires a high-low pressure difference. Because of this, the oil was supplied through the gap between the face and the face.Therefore, the parts D and E enclosed by oblique lines shown in FIG. Since the pressure difference between the upper and lower end surfaces E of the projecting end of the blade B 1 intervening in the receiving groove C 1 of the support C is unlikely to occur, the flow of the lubricating oil And lubrication failure occurs in these portions D and E, and therefore, the sliding contact portions of the above-mentioned opening rollers B and B1 with the above-mentioned fusing surfaces cannot be reliably lubricated, resulting in low reliability. There was a problem.

Disclosure of the invention

An object of the present invention is to provide an oscillating rotary compressor capable of reliably lubricating the entire surfaces of both ends in the axial direction of a roller and a blade and improving reliability.

In order to achieve the above object, an oscillating rotary compressor of the present invention includes: a cylinder having a cylinder chamber formed therein;

A roller fitted into the eccentric part of the driving mechanism and rotatably mounted inside the cylinder chamber;

A blade protruding integrally with the roller and dividing the cylinder chamber into a compression chamber and a suction chamber;

A support having a receiving groove, which is swingably disposed in the cylinder, and which freely receives a protruding end portion of the blade to advance and retreat;

An oil groove formed on the axial end surface of the blade and the blade protruding base of the mouth, one end of which is open to the inner peripheral surface of the roller, and the other end of which is open to the protruding end of the blade. And

In the rotary compressor having the above configuration, the lubricating oil supplied to the inner peripheral side of the roller flows through the oil groove due to the centrifugal force acting on the roller at the time of its orbital drive, and flows toward the tip end of the blade. Is forcibly guided. At this time, the lubricating oil flowing through the oil groove is supplied from the oil groove to the axial end face of the blade projecting base portion of the roller and the axial end face of the blade by the revolution drive of the roller. is there. Therefore, the entire end face of the roller and the blade in the direction of the cross section is formed by the inner peripheral surface of the roller and the compression chamber and the suction chamber. Combined with differential pressure lubrication utilizing the differential pressure generated between them, lubrication can be ensured and its reliability can be improved.

In one embodiment of the present invention, a high-pressure chamber closed to the outside of the cylinder is formed on the back side of the blade in the receiving groove of the support. In other words, a high-pressure chamber communicating with the inner peripheral side of the roller 1 through the oil groove is formed on the back side of the blade. Therefore, the lubricating oil introduced from the oil groove into the high-pressure chamber can be filled in the high-pressure chamber during the revolution IE of the roller, and therefore, the suction chamber maintained in a low-pressure state with respect to the high-pressure chamber. On the other hand, the pressure can be caused to flow by the differential pressure along the suction chamber-side outer peripheral portion of the support supported in the cylinder and the suction chamber side wall of the blade. On the other hand, on the compression chamber side, the lubricating oil in the high pressure chamber is compressed by the differential pressure of the support until the gas fluid compressed therein becomes equal to the internal pressure of the high pressure chamber. The air can be flowed to the compression chamber along the outer peripheral portion on the chamber side or along the side wall of the compression chamber of the blade. As a result, it is possible to effectively lubricate the outer peripheral portion and both end surfaces of the support and the receiving groove.

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a perspective view of a conventional roller integrally formed with a blade. FIG. 2 is a perspective view showing a compression element including a roller 1 in the oscillating rotary compressor according to the first embodiment of the present invention.

FIG. 3 is a plan view showing a main part of the first embodiment.

FIG. 4 is a plan view showing a main part of the second embodiment of the present invention.

FIG. 5 is a longitudinal sectional view showing the overall structure of a horizontal rotary compressor according to a third embodiment of the present invention.

FIG. 6 is a sectional view showing a main part of the third embodiment. BEST MODE FOR CARRYING OUT THE INVENTION

FIGS. 2 and 3 show only the compression element portion of the oscillating rotary compression contact of the first embodiment, which is closed by the face surfaces of the front and rear heads (not shown). A roller 2 integrally provided with a blade 21 protruding radially outward in the cylinder chamber 11 of the cylinder 1 is attached to the roller 2 and the upper and lower end surfaces of the blade 21 with the above-mentioned respective heads. The eccentric part 31 of the drive shaft 3 is inserted into the roller 2 while being slidably in contact with the fuser surface, and the roller 2 is rotated with the rotation of the drive shaft 3 so that the outer peripheral surface of the roller 2 is rotated. The revolving drive is performed while making contact with the inner wall surface of the cylinder chamber 11. On the other hand, an intermediate portion between the discharge port 12 and the suction hole 13 provided in the cylinder 1 is provided inside the cylinder chamber 11. A circular support hole 14 communicating with the support hole 14 is formed. The support 4 slidably in contact with each of the above-mentioned heads is rotatably supported, and the receiving groove 41 provided in the support 4 supports the distal end side of the blade 21 so as to swing and advance and retreat. ing. The support 4 is formed of two semi-cylindrical members 4A and 4B, and the flat portion between the flat surfaces of the members 4A and 4B is defined as the receiving groove 41. The leading end of the blade 21 is inserted into the receiving groove 41.

When the roller 2 is driven to revolve, the cylinder chamber 1 surrounded by a contact whose outer peripheral surface is in contact with the inner wall surface of the cylinder chamber 11 and the front wall surface of the blade 2 1 in the revolving direction of the roller 2. The interior space 1 is not provided with the suction chamber Y communicating with the suction hole 13, and the inside of the cylinder chamber 11 is surrounded by the contact point and the rear wall surface of the blade 2 2 in the revolving direction of the roller 2. As the compression chamber X communicating the space with the discharge □ 12, by moving the contact point of the roller 2 along the inner wall surface of the cylinder chamber 11 while driving the drive shaft 3, Above suction hole 13 The gas is sucked into the suction chamber Y, and the gas is compressed in the compression chamber X and discharged from the discharge port 12 so that the suction and compression of these gases are repeated.

Further, an oil supply passage 32 communicating with the oil supply pump is formed inside the center of the drive shaft 3 and extends outward from the lined oil passage 3 2 in the eccentric portion 31 of the IS drive shaft 3 in the strange direction. A branch passage 33 is provided, and high-pressure lubricating oil pumped into the lined oil passage 32 is passed through the branch passage 33 between the inner peripheral surface of the roller 2 and the outer peripheral surface of the eccentric portion 31. Oil is supplied to the sliding contact area.

When the roller 2 revolves, the high-pressure lubricating oil pumped up by the oil supply pump is supplied to the inner peripheral side of the roller 2 to have a high pressure. Therefore, the inner peripheral side of the roller 2 And a predetermined pressure difference is always generated between the suction chamber Y and the compression chamber X. On the compression chamber X side, the gas fluid flows in the compression chamber X with the pressure on the inner peripheral side of the roller 2. Until compressed to the same pressure, a predetermined height differential pressure is generated between the inner peripheral portion and the inner peripheral portion. As a result, the high-pressure lubricating oil supplied to the inner peripheral portion of the roller 2 is supplied from the inner peripheral side of the roller 2 to the compression chamber X and the suction chamber Y as shown by a solid line arrow n in FIGS. When the lubricating oil is introduced into the compression chamber X and the suction chamber Y through the upper and lower ends of the roller 2, the lubricating oil is supplied to the upper and lower ends of the roller 2 as the roller 2 revolves.

In the embodiment shown in FIG. 2.3, in the above configuration, one end of the roller 2 is attached to the upper and lower end surfaces of the blade protruding base and the upper and lower end surfaces of the blade 21. A linear oil groove 22 was formed on the peripheral surface, and the other end was released toward the protruding tip side of the blade 21.

Therefore, it is pumped into the oil supply passage 32 of the drive shaft 3 and the branch passage 3 As shown by the solid arrow p in Fig. 2.3, the lubricating oil that has been supplied to the sliding contact area between the roller 2 and the eccentric part 3 1 from above is the centrifugal force generated when the roller 2 revolves. The lubricating oil that is forcibly guided along the oil grooves 22 to the protruding tip side of the blade 21 and flows through the oil grooves 22 is revolved by the rollers 2 so that the lubricating oil flows out of the oil grooves 22. Oil is supplied to the upper and lower end surfaces of the roller 2 at the protruding base of the blade and the upper and lower end surfaces of the blade 21.

As a result, the entire upper and lower end surfaces of the roller 2 and the blade 21 can be reliably lubricated, and the reliability can be improved. In the embodiment of FIGS. 2 and 3 described above, the protruding tip side of the blade 21 in the receiving groove 41 of the support 4 is opened, but it is closed to the outside of the cylinder 1. In any case, the entire upper and lower end surfaces of the roller 2 and the blade 21 can be surely lubricated.

Further, the second embodiment shown in FIG. 4 is characterized in that the two members 4 A, 4 B The high-pressure chamber 15 continuous with the receiving groove 41 formed therebetween and communicating with the inner peripheral side of the roller 2 via the oil groove 22 provided in the blade 21 is formed as described above. It is formed in a closed shape to the outside of the cylinder 1.

In the above configuration, when the roller 2 revolves in the direction in which the blade 21 advances to the high-pressure chamber 15, the inner peripheral portion of the roller 2 is lubricated by the centrifugal force of the roller 2. The high-pressure lubricating oil thus introduced is introduced into the high-pressure chamber 15 via the oil groove 22 and is filled with the high-pressure lubricating oil. Therefore, as shown by a dotted arrow q in FIG. The lubricating oil in the high-pressure chamber 15 is moved by the differential pressure, The gas flows toward the suction chamber Y along the suction chamber-side outer periphery of the support 4 and the suction chamber side wall of the blade 21. On the other hand, in the compression chamber X, the lubricating oil in the high-pressure chamber 15 is subjected to a differential pressure until the gas fluid compressed therein becomes equal to or higher than the internal pressure of the high-pressure chamber 15. It flows to the compression chamber X along the compression chamber-side outer peripheral portion of the support 4 and the compression chamber side wall of the blade 21, and thus flows from the high-pressure chamber 14 to the compression chamber X and the suction chamber Y. Oil can be supplied to the outer peripheral portion, upper and lower end surfaces, and the receiving groove 41 of the support 4 by the oil flow due to the differential pressure of the above, and the outer peripheral portion, upper and lower end surfaces of the support 4 and the blade 21 slide. Lubrication of the receiving groove 41 can also be effectively performed.

FIG. 5 shows the overall structure of a high-pressure dome-shaped horizontal rotary compressor according to a third embodiment, which is located on one side in the longitudinal direction inside a horizontal casing 101 having an oil sump 0 at the inner bottom. A motor 102 composed of a stay 1 2 1 and a rotor 1 2 2 is provided, and a drive shaft 10 extending from the opening 1 2 2 is provided on the other side inside the casing 101. A compression element 104 driven by 3 is provided. This compression element 104 is composed of a cylinder 105 having a cylinder chamber 15 1 therein, a front head 106 and a rear head 1 disposed on both axial sides of the cylinder 105. 07.

As shown in FIG. 6, the cylinder chamber 150 of the cylinder 105 has a cylindrical roller 108 into which the eccentric part 131 of the driving vehicle 103 is inserted. The compression chamber X communicating with the discharge port 15 2 provided in the cylinder 105 and the suction chamber communicating with the suction port 15 3 A blade 109, which is defined as Y, is integrally protruded radially outward from an outer peripheral surface of the roller 108, and the blade 109 is rotatably provided on the cylinder 105. It is swingably supported on the support 110.

Then, with the rotation of the drive shaft 103, the roller 108 is rotated. Revolving in the cylinder chamber 151, the fluid gas introduced from the suction pipe 10la connected to the suction port 1553 is sucked into the suction chamber Y, compressed in the compression chamber X, The compressed gas is discharged from the discharge port 152 to the internal space of the casing 101 through the inside of the muffler 161, which is provided outside the front head 106, and A discharge pipe 10 lb opened to the motor 102 side inside the thing 101 is discharged to the outside. In the horizontal rotary compressor of the present embodiment, the blade 109 is disposed obliquely on the upper side of the cylinder 105 away from the oil reservoir 0 of the casing 101. Then, an oil chamber 154 serving as a closed space for supplying oil to the blade 109 is formed on the back side of the blade 109, and the high-pressure oil lined up in the compression chamber X is supplied to the above-described high-pressure oil. Due to the pressure difference between the suction chamber Y and the suction chamber Y, the oil is introduced into the oil chamber 154 through a gap formed between the blade 109 and the support 110, and is introduced into the oil chamber 154. The introduced oil is further led to the suction chamber Y through a gap formed between the blade 109 and the support 110, and the oil is introduced and led to slide the blade 109. The parts are lubricated. As described above, the oil supply to the blade 109 can be performed from the oil chamber 154 provided on the back side of the blade 109, so that the blade 109 does not need to be moved to the oil reservoir 0, The blade 109 can be set at an arbitrary position of the cylinder 105. As a result, as shown in FIG. 5, the blade 109 can be disposed on the upper side of the cylinder 105 separated from the oil reservoir 0. As a result, the discharge port 152 and the suction port 1553 provided in the vicinity of the blade 109 can also be formed at a position separated from the oil reservoir 0, and the high-temperature oil in the oil reservoir 0 It is possible to prevent the suction gas sucked from the suction port 153 from being overheated, so that a decrease in volumetric efficiency can be reduced and the performance can be improved. Moreover, the blade 109 is connected to the cylinder 1 By disposing the suction port on the upper side of the oil reservoir 0 in the cylinder 105, the suction port 153 can be formed above the oil reservoir 0. When connecting 101a, the suction pipe 101a can be easily connected from one side in the lateral direction of the casing 101, and the assembling workability can be improved. There is no need to separately secure a space for connecting the suction pipe 101a to the side, and the mounting height of the casing 101 can be reduced.

In addition, one end in the length direction is opened to the inner peripheral surface of the roller 108, and the other end is opened to the upper and lower end surfaces of the blade protruding base of the upper blade 109 and the roller 108, respectively. An oil groove 111 is formed in the oil chamber 154 provided on the back side of the blade 109 so as to open in a radial direction and extend in a radial direction. By providing the oil groove 111, the lubricating oil supplied from the oil reservoir 0 to the sliding portion of the roller 108 is moved by the centrifugal force generated by the revolution of the roller 108. Since the oil chamber 154 can be positively refilled with oil through the step 111, the oil chamber 154 can always be filled with high-pressure oil, so that there is no shortage of oil. In addition, since the oil chamber 154 can always be set at a high pressure with high-pressure oil, the oil chamber 154 is supported in the cylinder 105 on the suction chamber Y side maintained at a low pressure state with respect to the oil chamber 154. The lubricating oil can be caused to flow by the differential pressure through the gap between the support 110 and the blade 109, and the gas fluid compressed inside the compression chamber X is compressed by the oil in the compression chamber X side. Until the internal pressure of the chamber 154 becomes equal to the internal pressure, the wide lubricating oil in the oil chamber 154 is released by the pressure difference through the gap between the support 110 and the blade 109. Thus, it is also circulated to the compression chamber X. As a result, since the lubrication of the blade 109 can be performed more reliably, the lubrication performance of the blade 109 can be enhanced. Industrial applicability

The oscillating rotary compressor of the present invention is mainly used for a refrigeration system.

Claims

Billing IS box

1. A cylinder (1.1 05) with a cylinder chamber (11, 151) formed inside,

A roller (2, 108) fitted to the eccentric part (31, 131) of the drive shaft (3, 103) and revolving inside the cylinder chamber (11, 151);

A blade (21, 109) integrally protruding from the roller (2, 108) and dividing the cylinder chamber (11.1 51) into a compression chamber (X) and a suction chamber (Y); and the cylinder (1.105) A support (4, 110) having a receiving groove (41) that is swingably disposed therein and that freely receives the protruding tip portion of the blade (21, 109).

The blade (21.109) and the roller (2.108) are formed on the axial end surface of the blade projecting base, and one end is opened to the inner peripheral surface of the roller (2, 108) and the other end is formed. An oscillating rotary compressor having an oil groove (22.111) opened at the protruding tip of the blade (21.109).

2. In the oscillating rotary compressor according to claim 1,

In the receiving groove (41) of the support (4, 110), on the back side of the blade (21, 109), a high-pressure chamber (15, 154) closed to the outside of the cylinder (1, 105). Swing type rotary compressor in which is formed.