JP4301119B2 - Scroll compressor - Google Patents

Description

The present invention relates to a tip seal of a scroll compressor used for an air conditioner or the like.

  Hereinafter, an oil supply system to the compressor mechanism of a conventional scroll compressor and the function of the tip seal will be described with reference to the drawings.

  FIG. 6 is a longitudinal sectional view of a conventional scroll compressor, and FIG. 7 is a partial sectional view of the compression mechanism.

  A compression mechanism and a stator 203a of an electric motor that drives the compression mechanism are fixed inside an airtight container 201 having an oil reservoir 207 that stores lubricating oil at the bottom, and a crankshaft that drives the compression mechanism to a rotor 203b of the electric motor An oil reservoir 207 is formed around the compression mechanism of the sealed container 201. The compression mechanism includes a fixed scroll 210, a turning scroll 213 that meshes with the fixed scroll 210 to form a plurality of compression chambers 214, a rotation restraining component 215 that prevents the turning of the turning scroll 213 and makes only turning, An orbiting drive shaft 222 provided on the opposite side of the orbiting scroll 213, an eccentric bearing 223 provided inside the main shaft 218 of the crankshaft 206 and fitted with the orbiting drive shaft 222, and a main shaft 218 of the crankshaft 206. A bearing part 221 having an axial movement limiting flat surface portion 226 for limiting the axial movement of the orbiting scroll 213 is disposed with a small gap from the main bearing 219 to be supported and the back of the end plate 224 behind the orbiting scroll 213. To do. A sliding partition ring 225 that divides the gas pressure applied to the end plate back surface 224 into a discharge pressure applied to the central portion and a pressure lower than the discharge pressure applied to the outer periphery of the end plate back surface 224 is disposed on the axial movement restriction plane portion 226. . The back pressure chamber 245 formed in the space outside the sliding partition ring 225 is the center of the orbiting scroll end plate back surface 224 via a first communication passage 241 having a throttle mechanism 246 provided inside the orbiting scroll end plate 213. It is the structure which communicates with the space 249 where the discharge pressure of a part acts.

  Further, a second communication passage 248 formed in the inside of the orbiting scroll end plate 227 and communicating with the tip seal storage groove 251 is branched from the middle of the first communication passage 241 communicating with the back pressure chamber 245. The throttle mechanism 246 is provided in the downstream first communication passage.

  Further, the crankshaft 206 is also provided with an oil supply passage 243 penetrating the crankshaft 206. An end surface of the oil supply passage 243 on the side opposite to the compression mechanism is an oil reservoir 207 via an oil pump 242, and an end surface on the compression mechanism side is an orbiting scroll end plate. It is configured to communicate with a space 249 in which the discharge pressure at the center of the back surface 224 acts.

  With this configuration, the lubricating oil guided from the oil reservoir 207 to the space 249 in which the discharge pressure at the center of the orbiting scroll end plate back 224 acts by the oil pump 242 or the like is throttled from the first communication passage 241. An appropriate amount is supplied to the outermost compression chamber via the mechanism 246 and is formed in the clearance on the back surface of the chip seal storage groove 251 and the chip seal 244 from the second communication path 248 branched from the first communication path 241. By being sufficiently supplied to the space, the leakage path to the low pressure side formed in the longitudinal direction of the tip seal storage groove 251 is blocked, and the compression chamber is formed by the lubricating oil overflowing from the tip seal storage groove 251. It was the oil supply composition which also supplies to the wall surface.

Further, as shown in FIG. 5, the tip seal 244 is formed with an appropriate length in the longitudinal direction shorter than the tip seal storage groove 251, and a gap 270 is formed at the winding start end to form the tip seal storage groove 251. Since the swivel scroll 213 is swung, the swivel movement of the orbiting scroll 213 causes the discharge pressure to be introduced to the back surface of the tip seal 244 when the winding start end clearance 270 communicates with the discharge hole 260, and is pressed against the bottom surface of the fixed scroll 210. The leakage passage to the lower pressure compression chamber formed outside across the tip seal 244 is blocked.
JP 2000-213477 A

  However, in the above-described conventional configuration, the tip is reduced due to a pressure drop due to passage resistance in the downstream portion (winding end portion or suction side) more than half a turn from the opening end 252 of the discharge hole 260 and the second communication passage 248 on the tip seal storage groove side. Since the ability to float the seal 244 is reduced and the compression chamber 281 on the outer side of the chip seal has a higher pressure (see FIG. 4) than the inner compression chamber 282, the chip seal 244 is placed in the chip seal storage groove. As a result of being twisted and pressed against the inner and outer walls of 251, the end of winding of the tip seal 244 is caught and the floating becomes insufficient, and the tip seal 244 crosses the tip seal 244 and leaks into the compression chamber on the lower pressure side, resulting in reduced performance. Had problems.

  As a measure for improving this, there is a case where the position of the open end 252 of the second communication passage 248 is installed on the winding end side. In this case, the pressure difference between both ends of the second communication passage 248 becomes large. The high-pressure and high-temperature lubricating oil excessively leaks into the compression chambers 281 and 282 in the vicinity of the suction chamber via the chip seal storage groove 251, so that there is a problem that the performance is also deteriorated due to the overheat loss of the suction refrigerant. It was.

  The present invention solves such conventional problems, and an object thereof is to provide higher performance as a compressor.

  In order to solve the above-mentioned problems, the present invention has a chip seal cross-sectional shape in which a chamfered relief portion is provided on the outer side of the anti-seal surface of the chip seal that is installed in the approximately half-turn section from the winding scroll end to the winding start side. In addition, the size of the escape portion is increased as it goes to the end of the winding.

By adopting the tip seal cross-sectional shape as described above , pressure is introduced from the outer compression chamber to the chamfered relief portion on the winding end side where the pressure is higher in the outer compression chamber of the tip seal, and the escape is performed. By increasing the size of the part toward the winding end side, the passage resistance loss is reduced, and the pressure introduced from the discharge hole or the second communication path is acted on the winding end tip seal without being attenuated. This improves the floatability of the chip seal and increases the compression efficiency.

  The scroll compressor of this invention can provide the scroll compressor which ensures high performance by making it the cross-sectional shape which improves the floating property and stability of a chip seal.

The scroll compressor according to the present invention has a tip seal cross-sectional shape in which a chamfered relief portion is provided on the outer side of the seal surface of the tip seal that is installed in an approximately half-winding section from the winding scroll end to the winding start side. By increasing the size of the portion toward the end of the winding, pressure is introduced from the outer compression chamber to the chamfered escape portion on the winding end side having a timing when the pressure of the outer compression chamber of the tip seal becomes higher, and The passage resistance loss is reduced by increasing the size of the relief portion toward the winding end side, and the pressure introduced from the discharge hole or the second communication passage is acted on the winding end tip seal without being attenuated. Thus, the floatability and stability of the tip seal are improved, and the compression efficiency can be increased.

(Embodiment 1)
Embodiments of the present invention will be described below with reference to the drawings.

  6, 7, and 3, a compression mechanism and a stator 203 a of an electric motor that drives the compression mechanism are fixed inside a sealed container 201 having a discharge pressure atmosphere having an oil reservoir 207 that stores lubricating oil at the bottom, and rotation of the electric motor is performed. A crankshaft 206 for driving the compression mechanism is coupled to the child 203b, and an oil reservoir 207 is formed around the compression mechanism of the sealed container 201. The compression mechanism includes a fixed scroll 210, a turning scroll 213 that meshes with the fixed scroll 210 to form a plurality of compression chambers 214, a rotation restraining component 215 that prevents the turning of the turning scroll 213 and makes only turning, An orbiting drive shaft 222 provided on the opposite side of the orbiting scroll 213, an eccentric bearing 223 provided inside the main shaft 218 of the crankshaft 206 and fitted with the orbiting drive shaft 222, and a main shaft 218 of the crankshaft 206. A bearing part 221 having an axial movement limiting flat surface portion 226 for limiting the axial movement of the orbiting scroll 213 is disposed with a small gap from the main bearing 219 to be supported and the back of the end plate 224 behind the orbiting scroll 213. To do. A sliding partition ring 225 that divides the gas pressure applied to the end plate back surface 224 into a discharge pressure applied to the central portion and a pressure lower than the discharge pressure applied to the outer periphery of the end plate back surface 224 is disposed on the axial movement restriction plane portion 226. . The back pressure chamber 245 formed in the space outside the sliding partition ring 225 has a discharge pressure at the center of the orbiting scroll end plate back surface 224 via the first communication passage 241 provided inside the orbiting scroll end plate 213. It is configured to communicate with the acting space 249.

  Further, the second communication passage 248 formed in the inside of the orbiting scroll end plate 227 and communicating with the tip seal storage groove 251 is branched from the middle of the first communication passage 241 communicating with the back pressure chamber 245.

  Further, the crankshaft 206 is also provided with an oil supply passage 243 penetrating the crankshaft 206. An end surface of the oil supply passage 243 on the side opposite to the compression mechanism is an oil reservoir 207 via an oil pump 242, and an end surface on the compression mechanism side is an orbiting scroll end plate. It is configured to communicate with a space 249 in which the discharge pressure at the center of the back surface 224 acts.

  With this configuration, the lubricating oil guided from the oil reservoir 207 to the space 249 in which the discharge pressure at the center of the orbiting scroll end plate back 224 acts by the oil pump 242 or the like is throttled from the first communication passage 241. An appropriate amount is supplied to the outermost peripheral compression chamber via the mechanism 246 and the like, and is formed in the clearance on the back surface of the chip seal storage groove 251 and the chip seal 244 from the second communication path 248 branched from the first communication path 241. Is sufficiently supplied to the space where the chip seal storage groove 251 is formed, so that the leakage path to the low pressure side formed in the longitudinal direction of the chip seal storage groove 251 is blocked and the compression chamber is formed by the lubricating oil overflowing from the chip seal storage groove 251. The oil supply structure also supplies to the wall surface.

  Further, as shown in FIG. 5, the tip seal 244 is formed to have an appropriate length shorter in the longitudinal direction than the tip seal storage groove 251 and an appropriate amount of clearance 270 is formed at the winding start end. Since the swivel motion of the orbiting scroll 213 causes the winding start end clearance 270 to communicate with the discharge hole 260, the discharge pressure is introduced into the back surface of the chip seal 244 and is pressed against the bottom surface of the fixed scroll 210. The leak passage to the lower pressure compression chamber formed outside across the seal 244 is blocked.

  Further, as shown in FIGS. 1 and 2, the tip seal 244 assembled in the tip seal storage groove 251 has a chamfered portion on the outer side of the anti-seal surface in the approximately half-winding section from the turning scroll winding end 285 to the winding start side. The cross-sectional shapes 292a and b are provided with relief portions 286a and b. Furthermore, the size of the chamfered relief portions 286a and 286 becomes larger toward the end of the winding. That is, the relationship between the sizes of the relief portions is 286a ≦ 286b.

By making the chip seal cross-sectional shape as described above, the high-pressure lubricating oil that has flowed from the discharge hole 260 through the gap between the chip seal 244 and the bottom surface of the chip seal storage groove 251 increases the passage resistance loss that increases with distance. more chips the sealing flying property is deteriorated, decreasing the influence of the flow resistance loss by increasing the size of the chamfer-shaped relief portion as the winding end in sections with at least chamfered shaped relief portion, the tip seal is floating Receiving pressure to introduce . As a result, the tip seal 244 is pressed against the both side wall surfaces of the tip seal storage groove 251 by the pressure difference between the compression chambers 281 and 282 adjacent to the tip seal 244 from the end of the orbiting scroll winding 285 on the almost half winding start side. Even at the point (see FIG. 1), the tip seal 244 can be easily lifted by the chamfered relief portions 286 and 287 of the tip seal 244 without being caught on the wall surface of the tip seal storage groove 251.

  Further, when the lubricating oil is guided to the gap formed between the chamfered relief portions 286a and 286b of the chip seal 244 and the bottom surface 254 of the chip seal storage groove 251, and the lubricating oil moves to the end side of the chip seal winding By this reaction force, the chip seal 244 is pressed against the side wall surface of the chip seal storage groove 251 and the bottom surface 255 of the fixed scroll 210, and the sealing performance in the cross direction of the chip seal is maintained even at the end of winding. By continuously performing this action, it is possible to simultaneously block a path that leaks from the high pressure side to the low pressure side along the tip seal housing groove 251.

  As a result, it is possible to provide a scroll compressor in which the tip seal floats stably and higher performance is ensured.

  As described above, the scroll compressor of the present invention can provide a scroll compressor that ensures high performance by improving the floatability and stability of the chip seal, so that a refrigerator or an air compressor, It can also be applied to applications such as expanders.

The perspective view which shows the relative position relationship between the tip seal cross-sectional shape of the present invention and the orbiting scroll Enlarged view of the tip seal of the present invention viewed from the orbiting scroll side Enlarged sectional view of the compression mechanism of a conventional scroll compressor The figure explaining the timing when the compression chamber outside the tip seal becomes higher in pressure than the inner compression chamber Partial enlarged sectional view of the winding start portion of the scroll compression mechanism Longitudinal sectional view of a conventional scroll compressor Enlarged longitudinal sectional view of a compression mechanism of a conventional scroll compressor

DESCRIPTION OF SYMBOLS 201 Airtight container 202 Compression mechanism 203a, 203b Electric motor 206 Crankshaft 207 Oil reservoir 210 Fixed scroll 213 Orbiting scroll 214 Compression chamber 215 Rotation restraint component 218 Main shaft 219 Main bearing 221 Bearing component 222 Orbit drive shaft 223 Eccentric bearing 225 Sliding partition ring 241 First communication passage 242 Oil pump 244 Tip seal 245 Back pressure chamber 248 Second communication passage 251 Tip seal storage groove 252 Open end of second communication passage 253 Branch portion of communication passage 254 Tip seal storage groove bottom surface 255 Fixed Scroll bottom 260 Discharge hole 270 Tip seal winding start gap 281 Outermost peripheral compression chamber 282 outside tip seal 282 Outermost peripheral compression chamber 285 inside tip seal 285 End of orbiting scroll winding 286a, 286b Tip seal chamfer 92a, 292b tip seal cross-sectional shape

Claims (1)

There is an oil reservoir for storing lubricating oil at the bottom, and an electric motor and a compression mechanism driven by this electric motor are arranged inside a sealed container on which discharge pressure acts. The compression mechanism meshes with the fixed scroll and the fixed scroll. A rotating scroll that forms a plurality of compression chambers, a rotation restraint component that prevents the rotating scroll from rotating and only rotates, a crank shaft that drives the rotating scroll to rotate, and a main shaft formed on the crank shaft are supported. Orbiting drive, which is configured to include a bearing component having a main bearing that engages with an eccentric drive engagement portion provided on the crankshaft on the back surface of the orbiting scroll on the side opposite to the lap. An engagement portion is provided, and a pressure acting on the back surface of the end plate on the outer side of the turning drive engagement portion is applied to a discharge pressure acting on the center portion of the back surface of the end plate and an outer periphery of the back surface of the end plate. A sliding partition ring that divides into a pressure lower than the discharge pressure to be supplied, supplies high-pressure lubricating oil from the oil reservoir to the central part of the rear face of the end plate, and outwards of the central part of the rear face of the end plate and the outer side of the sliding partition ring And a back pressure chamber formed in the space of the orbiting scroll through a first communication passage formed inside the end plate of the orbiting scroll, branching from the middle of the first communication passage, And a second communication passage that communicates with the bottom surface on the winding start side from the center in the winding direction of the chip seal storing groove for storing the chip seal, and the outside of the tip seal is compressed on the winding end side of the chip seal. a scroll compressor having a timing towards the chamber becomes higher pressure than the inside of the compression chamber, said chip being installed in the approximate half-turn section toward the winding start side from the orbiting scroll winding end Providing a chamfer-shaped relief portion in the counter-sealing surface outside the seal has a tip seal cross-sectional shape, and a scroll compressor the size of the escape portion increases toward the winding end.