JP4184673B2 - Scroll compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention is used in a refrigeration cycle apparatus and the like, and has a simple structure, high performance and high reliability scroll compression. Machine It is to provide.
[0002]
[Prior art]
This type of conventional scroll compressor generally has a configuration as shown in FIG. In this device, the fixed spiral component 301 and the swirl spiral component 302 are engaged with each other to form a plurality of compression spaces 300 therebetween. The orbiting spiral component 302 is driven by the eccentric portion 309 of the crankshaft 306 and is caused to perform a circular orbit motion, that is, orbiting motion with respect to the fixed scroll 301. By reducing the volume while the compression space 300 moves from the outer peripheral side toward the center of the spiral by the swirling motion of the swirling spiral component 302, the refrigerant gas is sucked from the suction port 314 and compressed, and then the discharge port The liquid is discharged into the internal space 316 of the sealed container 304 through 315. Here, the fixed spiral component 301 and the swirl spiral component 302 described above are the main components, and the compression mechanism unit 310 is configured.
[0003]
The drive mechanism of the compression mechanism unit 310 is configured by connecting a crankshaft 306 in a penetrating manner to a rotor 305 of an electric motor 303 provided vertically with the compression mechanism unit 310 inside the sealed container 304. 306 is driven to rotate. The upper end portion of the crankshaft 306 is supported by the main bearing member 307 via the bearing 311, and the tip end portion of the crankshaft 306 that protrudes upward from the main bearing 308 performs an eccentric motion with respect to the swirl spiral component 302. An eccentric part 309 is provided for circular orbital movement via the slewing bearing 313. The lower end portion of the crankshaft 306 is supported by the auxiliary bearing member 317 via the auxiliary bearing 317a, and a positive displacement pump 318 is provided at the lower end of the crankshaft 306 that protrudes downward from the auxiliary bearing 317a.
[0004]
The positive displacement pump 318 is driven together with the compression mechanism 310 by the crankshaft 306, and sucks in lubricating oil (not shown) such as oil stored in the liquid reservoir 319 at the lower end of the hermetic container 304. The liquid is supplied to the liquid reservoir 321 through the liquid supply passage 320 formed in 306. The lubricating oil supplied to the liquid reservoir 321 lubricates and cools the slewing bearing 313, then lubricates the main bearing 308 through the next liquid reservoir 322, and then returns to the liquid reservoir 319 for recirculation. . On the other hand, a part of the lubricating oil supplied to the liquid pool part 321 is supplied to the back pressure chamber 329 while being decompressed by the throttle part 324 via the long hole 323 provided inside the swirl spiral part 302. Here, the liquid reservoirs 321 and 322 are high-pressure portions, and the back pressure chamber 329 is a high-pressure and low-pressure intermediate pressure portion, which are sealed by a seal member 328.
[0005]
The back pressure chamber 329 is supplied with the lubricating oil in the liquid pool 321 restricted to an appropriate amount by decompression by the throttling action of the throttling portion 324, and exerts a back pressure to back up the swirl spiral component 302, thereby rotating swirl spirals. The component 302 is pressed toward the fixed spiral component 301 so as not to be separated from the fixed spiral component 301 or to be overturned.
[0006]
As the lubricating oil supplied to the back pressure chamber 329 accumulates, the pressure in the back pressure chamber 329 rises and causes excessive contact between the swirl components 301 and 302, but the pressure is kept within a predetermined range. In order to maintain, a pressure adjustment mechanism 331 is provided between the back pressure chamber 329 and the suction area 300 a of the compression space 300. When the pressure in the back pressure chamber 329 becomes higher than the set pressure, the pressure adjusting mechanism 331 allows excess lubricating oil in the back pressure chamber 329 to escape to the suction area 300a and maintain the back pressure chamber 329 at a predetermined pressure. The role of the seal that prevents the swirl component 302 from excessively contacting the fixed swirl component 301 and the lubricating oil released to the suction area 300a is guided to the compression space 300 and prevents leakage of refrigerant gas and the like during compression. The contact surface of the fixed spiral component 301 and the swirl spiral component 302 serves to lubricate.
[0007]
A holding groove 334 that holds a tip seal 333 that branches from the upstream side of the narrowed portion 324 of the elongated hole 323 and seals between the swirl spiral component 302 and the fixed swirl component 301 provided at the tip of the blade. By providing the communication passage 335 (see, for example, Japanese Patent Publication No. 2000-213477), the lubricating oil is supplied to the space formed in the gap between the holding groove 334 and the back surface of the chip seal 333. As a result, a leakage path to the low pressure side formed in the longitudinal direction in the holding groove 334 is filled and blocked, and the lubricating oil overflowing from the holding groove 334 is formed outside across the right angle direction. The leakage passage to the low pressure compression space 300 is also blocked, and further supplied to the wall surface forming the compression space 300.
[0008]
Next, as shown in FIG. 9, the throttle portion 324 is a cylindrical pin having a screw portion 324a for attachment on the outer peripheral portion, and a narrow throttle hole 339 is provided at the center. The throttle unit 324 exerts a throttle action on the lubricating oil supplied from the liquid pool 321 to the back pressure chamber 329 through the elongated hole 323 through the throttle hole 339, and reduces the pressure to a proper amount and supplies the lubricant to the back pressure chamber 329. . This proper amount is adjusted by changing the inner diameter of the throttle hole 339.
[0009]
On the other hand, as another conventional scroll compressor, one having a configuration as shown in FIG. 10 is known (see Japanese Patent Laid-Open No. 7-77182). In this system, a lubricating oil is supplied using a differential pressure oil supply system in which when the back pressure becomes a certain value or more, the valve opens and excess input is released to the suction side. That is, the lubricating oil in the oil reservoir 319 at the bottom of the sealed container 304 is the difference between the pressure in the intermediate pressure chamber 342 at the back of the swirl spiral component 302 and the discharge pressure due to the discharged refrigerant filling the internal space 316 of the sealed container 304. The pressure is supplied to other sliding portions in the compression mechanism 310 including the main bearing member 307 and the swivel bearing 313 by pressure.
[0010]
The intermediate pressure chamber 342 is held at a pressure intermediate between the suction pressure and the discharge pressure by providing the swirl spiral component 302 with two intermediate holes (not shown) communicating with the intermediate pressure region of the compression space 300. Due to the pressure difference between the discharge pressure and the intermediate pressure, the lubricating oil passes through the oil supply path 320 of the crankshaft 306, the main bearing 308 as a sliding bearing, and the narrow oil supply groove 343 formed as a constricted portion therein, and the main bearing 308 and swivel. It is supplied to the intermediate pressure chamber 342 between the bearing 313, the main bearing member 307, and the swirl spiral component 302. The lubricating oil that has entered the intermediate pressure chamber 342 is supplied to the compression space 300 via the intermediate pressure hole and the outer peripheral portion of the swirl spiral component 302 and then discharged from the discharge port 315 together with the refrigerant gas to the sealed container inner space 316.
[0011]
A check valve 345 for preventing the refrigerant from flowing backward is provided in the suction passage 344 of the compression mechanism 310. The check valve 345 is shown in FIG. 11 when the scroll compressor is stopped, and in FIG. When the compressor is operated, the refrigerant gas enters the suction passage 344 from the external cycle, and the check valve 345 is pushed down from the position shown in FIG. 11 to the position shown in FIG. 12 by the suction gas pressure. A space communicating with the compression space 300 is formed. Thereby, the suction gas is sucked into the compression space 300 from the space and compressed. The compressed refrigerant gas is discharged from the discharge port 315 of FIG. 10 to the sealed container inner space 316, and the discharged high-pressure gas is notched provided in the outer peripheral portion of the compression mechanism 310 from the upper space of the sealed container 304. Or it passes through a communicating hole and is supplied to the lower space which accommodates the electric motor 303 etc. At this time, the refrigerant gas cools the stator of the electric motor 303 and further passes through a space such as the electric motor 303 to separate the lubricating oil discharged from the discharge port 315 in the form of a mist, thereby discharging the high-pressure refrigerant gas. Return from path 347 to the external cycle.
[0012]
When the operation of the compressor is stopped, the check valve 345 causes the high-pressure refrigerant gas that is in the process of returning to the external cycle from the compression space 300, the sealed container 314, and the discharge passage 347 to flow backward from the suction passage 344 to the upstream side. And the spring 348 provided at the lower stage of the check valve 345 is pushed back from the position of FIG. 12 to the position of FIG. 11, and the suction side is formed between the end face of the seal collar 349 and the flat face of the check valve 345. The communication passage is closed to prevent the reverse flow of the refrigerant, and the lubricating oil at the lower part of the compressor is an oil supply path 320 for the crankshaft 306, a swing bearing 313, a main bearing member 307, an intermediate pressure. It is prevented from being taken out of the compressor through the chamber 342, the intermediate pressure hole, the compression space 300, and the like.
[0013]
[Problems to be solved by the invention]
However, as in the conventional example shown in FIG. 8, through the long hole 323 and the branch passage 335 that always communicate the high pressure oil reservoir 321 and the bottom surface of the holding groove 334 of the tip seal 333 provided at the tip of the swirl spiral component 302. When the lubricating oil is supplied from the liquid pool 321 to the holding groove 334, the holding groove 334 is always connected to the liquid pool 321 and high-pressure lubricating oil is continuously supplied, so that it can be formed between the tip seal 333 in the holding groove 334. Excess lubricating oil flows excessively into the low pressure suction area 300a side of the compression space 300 through the gap in the longitudinal direction, and suction heating occurs, resulting in performance degradation. In order to solve this problem, if the supply amount of the lubricating oil is limited by narrowing the passage portion where the long hole 323 communicates with the holding groove 334 to limit the supply amount of the lubricating oil, the compression space 300 flows into the low pressure suction area 300a side. Even if the amount can be decreased, the compression efficiency is lowered and the life is shortened due to wear of the sliding portion.
[0014]
Further, when the throttle effect is improved by reducing the inner diameter of the throttle hole 339 of the throttle unit 324 or increasing the length thereof, the holding groove is limited by the amount that limits the amount of liquid supplied from the liquid reservoir 321 to the back pressure chamber 329. Even if it becomes easy to supply to 334, this only causes the suction heating. On the other hand, the supply restriction slows the pressure increase in the back pressure chamber 329, so that excessive lubricating oil can be prevented from escaping to the suction area 300a to reduce the problem of suction heating, but the inner diameter of the throttle hole 339 can be reduced. If the length is made smaller or the length is made longer, it will be easily blocked by dust existing in the lubricating oil, the performance and reliability of the compressor will be lowered, and the processing of the throttle hole 339 will become difficult and the cost will increase. There is.
[0015]
On the other hand, in the conventional example shown in FIG. 10, the oil supply mechanism is a simple one that does not include a positive displacement pump, so that the cost of parts can be reduced, and even if it is easy to supply an appropriate amount of lubricating oil to each part, In order to ensure high reliability, it is necessary to provide a check valve 345. If there is a lot of leakage on the sealing surface of the check valve 345, the gas flows backward, and at that time, the lubricating oil in the compression mechanism 310 is removed. There remains a problem that reliability is lowered due to lack of lubricating oil to be taken out and lubricated. Further, the problem remains that the check valve 345 becomes a refrigerant gas suction resistance during normal operation and the performance is deteriorated.
[0016]
The present invention solves such a conventional problem, and is a low cost, high efficiency, high reliability scroll compression. Machine The purpose is to provide.
[0017]
[Means for Solving the Problems]
In order to achieve the above-described object, the scroll compressor according to the present invention is configured such that a fixed spiral part and a swirl swirl part whose blades rise from the end plate mesh with each other to form a compression space therebetween, and the swirl swirl part has A compression mechanism that changes the volume while moving the compression space while moving in a circular orbit with respect to the fixed spiral component, and a back surface of the swirl spiral component with the swirl drive of the swirl spiral component by sucking, compressing and discharging the fluid In addition to supplying the liquid supplied to the liquid reservoir in the back pressure chamber on the back side of the outer periphery of the swirl swirl component through the swirl swirl component and restricting the supply, the liquid is supplied to the swirl swirl component through the swirl swirl component. A liquid supply mechanism that supplies a holding groove that holds a sealing member between the blade and the fixed spiral component at the tip of the blade, and in particular, the liquid supply mechanism is provided on a surface that slides with the swirl spiral component of the fixed spiral component Recess A first passage which is provided in the swirl spiral component and intermittently communicates with the recess as the swirl spiral component swivels and supplies the liquid in the liquid reservoir to the recess, and the swirl spiral component is provided with the swirl. The main feature is that a second passage is provided which communicates with the recess at a timing different from that of the first passage and supplies the liquid in the recess to the holding groove.
[0018]
In such a configuration, the swirl swirl component is driven to swivel and the suction, compression, and discharge operations are repeated, and the lubrication mechanism is activated to pass through the liquid pool at the back of the swirl swirl component, and the back of the swirl swirl component. Liquid is supplied to the back pressure chamber and the holding groove that holds the sealing member at the tip of the swirl spiral component blade, and the supply of liquid in the back pressure chamber is performed based on a predetermined restriction, so that the back of the swirl spiral component While a predetermined back pressure is applied to perform backup, supply to the holding groove is performed by supplying liquid in the liquid reservoir to the recess when the first passage is connected to the recess as the swirl spiral part is swung. Since the liquid in the recess is supplied to the holding groove through the second passage at a timing different from that of the first passage, and therefore at the timing when the first passage is no longer communicated with the first passage, the liquid is supplied to the holding groove at a high pressure. Supply is limited and excess liquid is likely to occur The amount of liquid that is easy to spread even in the high-pressure region of the holding groove at the boundary is reliably regulated by a recess that does not communicate with the first and second passages without being squeezed. It is possible to supply an appropriate amount of liquid to the entire compression space while suppressing outflow to the suction area side, and to achieve sealing and lubrication. A scroll compressor with high performance and reliability is indispensable. And can be provided as an inexpensive one. Further, even if the differential pressure oil supply method is adopted, one of the first and second passages is closed between the recesses and does not communicate with each other, so that the liquid continues to be supplied by the differential pressure remaining when the operation is stopped. There is no such thing as an excess supply of liquid and no take-out to the outside. Therefore, a check valve is not necessary.
[0019]
However, even if the intermittent communication of the first and second passages is made simultaneously with the recesses and the operation may be stopped in this state, the above-described refueling method using a positive displacement pump may be used. There is no problem of taking it outside.
[0020]
Further, the supply restricting portion of the liquid supply mechanism may be configured such that the swirl part of the swirling spiral component is provided in a passage provided with a passage for supplying liquid from the liquid reservoir to the back pressure chamber, or a passage having or not having the restriction portion. Any intermittent communication part may be used as long as it is intermittently communicated with the movement. In the latter case, in particular, it can be limited in any way by setting the time ratio and flow rate intermittently associated with the swirling of the swirling spiral part. Even when the supply restriction is increased to prevent excessive pressure and suction heating, the problem is that the diameter and diameter of the throttle hole are reduced or lengthened as before, and clogging is likely to cause clogging and performance and reliability are difficult. All of the problems of high cost are solved, and a scroll compressor with higher efficiency and lower cost is realized. In addition, by combining the throttle part, the throttle part is easy to process and does not cause clogging.Therefore, higher supply restriction can be suppressed to suppress pulsating flow due to intermittent supply without particularly increasing the cost. However, it can be easily achieved, and further stability of performance and further prevention of inhalation heating can be achieved.
[0021]
In the case where the supply restricting portion is intermittently connected to the passage, if the time for communication is set to be different from the time for the concave portion to communicate with the first passage, the supply pressure of the liquid to the concave portion is reduced. It is not lowered by the liquid supply for the pressure, and it becomes easier to ensure the supply of the liquid to the high pressure region of the holding groove.
[0022]
In addition, when the supply restricting portion is provided in the branch passage branched from the middle of the first passage, since the portion of the first passage is provided in common, the passage structure is simple and easy to process. Cost is further reduced.
[0023]
In addition, a pressure adjusting mechanism is provided for allowing excess liquid in the back pressure chamber to escape through the passage and maintaining the back pressure chamber at a predetermined pressure, and the relief passage is an opening that is intermittently communicated with the back pressure chamber as the swirling spiral component turns. It can be set as the structure which has.
[0024]
In such a configuration, it is also possible to maintain a more appropriate back pressure state by adopting back pressure adjustment with a simple method that allows excess liquid to escape and to escape through the path, while the escaped liquid is maintained at the differential pressure. Since it is supplied to the compression space by the method and used for sealing and lubrication there, the sealing and lubricating functions between the fixed and swirling spiral parts are further improved. Moreover, since the opening of the escape path is intermittently communicated with the back pressure chamber as the swirl swirl part swivels, it is not possible to supply the relieved liquid to the suction area for back pressure adjustment, and there is a problem of suction heating. It can be suppressed from occurring. In particular, by making the time for the relief path opening intermittently communicating with the back pressure chamber different from the time for intermittently communicating with the supply restricting section, the liquid passage to the pressure adjustment mechanism can be relieved even when the operation is stopped. Since it is always shut off at either the opening or the supply restricting portion, even if the differential pressure oil supply method is adopted, excessive supply of liquid or take-out to the outside does not occur. Therefore, a check valve is not necessary.
[0028]
Further objects and features of the present invention will become apparent from the following detailed description and drawings. Each feature of the present invention can be used alone or in combination in various combinations as much as possible.
[0029]
DETAILED DESCRIPTION OF THE INVENTION
A scroll compressor and its driving method according to an embodiment of the present invention will be described in detail with reference to FIGS. The present embodiment illustrates several cases of a scroll compressor for a refrigeration cycle that is a vertical type and includes an electric motor and a compression mechanism in a container, and the fluid to be handled is a refrigerant. In addition, lubricating oil such as oil is used as a liquid for lubrication and sealing of each part. However, the present invention is not limited to this, and the following description does not limit the description of the scope of claims.
[0030]
As shown in FIGS. 1 to 7, the scroll compressor driving method of the present embodiment is formed by meshing the fixed spiral plate 10 a and the fixed spiral component 10 whose blades rise from the swivel mirror plate 25 and the swirl spiral component 11. The compressed space 32 performs the suction and compression of the refrigerant from the external cycle, and the discharge to the external cycle by changing the volume along with the movement when the swirl spiral component 11 is circularly orbitally moved with respect to the fixed spiral component 10. . At the same time, as the swirl swirl component 11 is swiveled, the liquid reservoir 21 or 22 on the back of the swirl swirl component 11, and in the example shown in the figure, the lubricating oil 41 supplied to the liquid reservoir 21 is supplied to the outer periphery of the swirl swirl component 11. The lubricant 41 is fed back to the swirl spiral component 11 through the swirl spiral component 11 while being supplied to a predetermined restriction base through the swirl spiral component 11 on the back side, and the fixed swirl component 10 at the tip of the blade of the swirl spiral component 11 It is supplied to a holding groove 34 for holding a chip seal 33 which is an example of a sealing member between the fixed and swivel spiral components 10 and 11 and is lubricated. In addition to this, in particular, the supply of the lubricating oil 41 to the holding groove 34 is performed at the time of intermittent direct or indirect communication between the liquid reservoir 21 and the holding groove 34 accompanying the turning of the swirl spiral part 11.
[0031]
As described above, the swirling spiral component 11 is swung in the compression space 32 between the stationary spiral component 10 and the suction, compression, and discharge operations are repeated. The liquid is supplied to the back surface side of the outer peripheral portion of the swirl spiral component 11 and the holding groove 34 of the tip seal 33 at the blade tip of the swirl spiral component 11 through the liquid reservoir 21 and the swirl spiral component 11 on the rear surface of the swirl spiral component 11. On the back side of the outer periphery of the swirl swirl component 11, the back-up of the swirl swirl component 11 with back pressure caused by the supplied liquid can be used to supply the lubricating oil 41 on the basis of a predetermined limit, thereby reducing the excess or deficiency of backup. In this way, a stable swiveling operation that does not leave the fixed spiral component 10 and does not contact excessively is ensured, while the holding groove 34 fixes and swirls each of the spiral components 10, 1, fixed by the supplied lubricating oil 41. The aim of sealing and lubrication between, compression performance, enhanced durability.
[0032]
In particular, the supply of the lubricating oil 41 to the holding groove 34 is caused by the high pressure in the liquid reservoirs 21 and 22 during intermittent direct or indirect communication between the liquid reservoir 21 and the holding groove 34 accompanying the swirling of the swirling spiral component 11. In addition, by supplying the lubricating oil 41 in an environment where the supply for back pressure is limited and excess liquid is likely to be generated without being squeezed, it is easy to spread even in the high pressure region of the holding groove 34, As a whole, the amount of the lubricating oil 41 to be supplied is regulated by setting the flow rate or the time ratio for the liquid reservoir 21 and the holding groove 34 to communicate with each other. An appropriate amount of liquid can be supplied to the entire region including the high pressure region to lubricate the seal of the compression space 32 and the sliding portion, and a scroll compressor with high performance and reliability can be obtained. In addition, it is realized at low cost without using special members or mechanisms by using essential members or existing members.
[0033]
A recess 38 on the fixed spiral component 10 side as an example of a liquid pool space as illustrated in FIGS. 1 to 7 between each of the spiral components 10 and 11 for fixing and rotating the indirect communication is illustrated in FIG. As shown in b), the liquid reservoir 21 and the holding groove are communicated at different timings. In this way, when the concave portion 38 communicates with the liquid reservoir 21, an appropriate amount of liquid in an environment where excess liquid is liable to be generated is received and confined, and when the concave portion 38 communicates with the holding groove 34, that is, the squeezing action. By supplying the oil without accompanying, the lubricating oil whose amount is more surely controlled in proportion to the capacity of the recess 38 can be supplied to the holding groove 34, while further suppressing the outflow to the low pressure suction area 30 side and the suction heating. In addition, the performance can be further improved by guaranteeing the supply of the holding groove 34 to the high pressure region.
[0034]
Further, with such a configuration, even when the differential pressure oil supply method is adopted, the communication is always cut off at either the liquid reservoir 21 side or the holding groove 34 side in the recess 38, and when the operation is stopped The lubricating oil 41 is not continuously supplied due to the remaining differential pressure, and the lubricating oil 41 is not excessively fed and taken out to the outside. Therefore, a check valve is not necessary.
[0035]
In the scroll compressor according to the present embodiment adopting the above driving method, the fixed spiral component 10 and the swirl spiral component 11 are engaged with each other as shown in FIGS. 1 and 2, and a compression space 32 is formed therebetween. When the swirl swirl component 11 is circularly orbitally moved with respect to the fixed swirl component 10, the compression mechanism 32 changes the volume while moving the compression space 32 and sucks, compresses and discharges the refrigerant, and the swirl swirl component The lubricating oil 41 supplied to the liquid pool 21 on the back surface of the swirl spiral component 11 in accordance with the swivel drive 11 is restricted by the supply restricting portion 101 through the swirl spiral component 11 to the back pressure chamber 29 on the back side of the outer periphery of the swirl spiral component 11. The lubricating oil 41 is supplied to the holding groove 34 for holding the sealing member such as the tip seal 33 at the tip of the swirl spiral component 11 through the swirl spiral component 11. The liquid supply mechanism 102 further includes a recess 38 provided on a surface of the stationary spiral component 10 that slides with the swirl spiral component 11, and a swirl spiral component 11 that swirls the swirl spiral component 11. Accordingly, the first passage 36 that intermittently communicates with the concave portion 38 and supplies the lubricating oil 41 of the liquid reservoir 21 to the concave portion 38, and the first passage 36 that is provided in the swirl spiral component 11 and that rotates with the first passage 36. It is sufficient to have a second passage 37 that communicates with the concave portion 38 at different timings and supplies the liquid in the concave portion 38 to the holding groove 34, and has high performance and high performance using essential members and existing members. A scroll compressor with a simple and inexpensive structure can be obtained. Here, the first and second passages 36 and 37 and the recess 38 form an intermittent supply mechanism 100 that intermittently supplies lubricating oil from the liquid reservoir 21 to the holding groove 34.
[0036]
However, even if the intermittent communication of the first and second passages 36 and 37 in the intermittent supply mechanism 100 is performed simultaneously with the recess 38 and the operation is stopped at the time of communication, the example of FIG. If it is an oil supply system using the positive displacement pump 18 as shown in Example 6, there is no problem of taking it out to the outside. Although not shown in the drawing, the direct communication between the first and second passages 36 and 37 is such that both are connected by the swirl spiral component 11, and the valve member that opens and closes the boundary portion is fixed to the fixed spiral component 10. And opening and closing by the relative movement of the swirl spiral part 11. However, other methods may be used.
[0037]
Further, the supply restricting portion 101 of the liquid supply mechanism 102 is provided in a long hole 23 as in the example of FIGS. 1 and 2, which is a passage for supplying the lubricating oil 41 from the liquid reservoir 21 to the back pressure chamber 29. The throttle part 24 provided, or the throttle part 24 as shown in FIG. 3 and FIG. What is necessary is just the intermittent communication part 103 etc. which are made to communicate with the back pressure chamber 29 intermittently with an exercise | movement.
[0038]
In the latter case, in particular, it can be limited in any way by setting the time ratio or flow rate intermittently or indirectly associated with the swirling of the swirling spiral component 11, and supplied to prevent excessive back pressure and suction heating. Even when the limit is increased, both the problem that the diameter and diameter of the throttle hole are reduced and lengthened, and the performance and reliability are reduced, and the problem that processing is difficult and costly are solved. A more efficient and low cost scroll compressor is realized. Further, as shown in the examples of FIGS. 3 and 4, by having the throttle portion 24 together with the intermittent communication portion 103, the throttle portion 24 is easily processed and does not cause clogging. Therefore, the cost is particularly increased. Without this, higher supply restriction can be easily achieved while suppressing pulsating flow due to intermittent supply, and further stability of performance and further prevention of suction heating can be achieved.
[0039]
When the supply restricting portion 101 is intermittently connected to the back pressure chamber 29 such as the long hole 23 as a passage as in the example shown in FIGS. If the timing is set to be different from the time for communicating with the first passage 36, the supply pressure of the lubricating oil 41 to the recess 38 is not lowered by the supply of the lubricating oil 41 for the back pressure, and the high pressure region of the holding groove 34 It becomes easier to secure the supply of the lubricating oil 41 to.
[0040]
Further, as shown in the example of FIG. 5, when the supply restriction unit 101 is provided in a branch passage branched from the middle of the first passage 36, a part of the first passage 36 is provided in common. Therefore, the passage structure is simple and easy to process by the shared amount, and the cost is further reduced.
[0041]
Further, as in each example shown in FIGS. 1 to 7, a pressure adjusting mechanism 31 is provided for allowing excess liquid in the back pressure chamber 29 to escape through the liquid escape path 104 and maintaining the back pressure chamber 29 at a predetermined pressure. In addition, as shown in FIGS. 6 and 7, the liquid escape path 104 is an opening that intermittently leads to the back pressure chamber 29 as shown in FIGS. 50. In this way, it is possible to maintain a more appropriate back pressure state by adopting a back pressure adjustment in a simple manner in which excess lubricating oil 41 is released through the passage 104, while the released lubricating oil 41 is removed. Since the pressure is supplied to the compression space 32 by the differential pressure method and used for sealing and lubrication there, the sealing and lubrication functions between the fixed and swirling spiral parts 10 and 11 are further improved. In addition, since the opening 50 of the liquid escape path 104 is intermittently communicated with the back pressure chamber 29 as the swirl spiral part 11 swivels, the lubricating oil 41 released for back pressure adjustment is supplied to the suction area 30 of the compression space 32. It is possible to suppress the problem of inhalation heating that is not performed without darkness. In particular, the time during which the opening 50 of the liquid escape passage 104 is intermittently communicated with the back pressure chamber 29 is different from the time during which the opening 50 is intermittently communicated with the supply restriction unit 101, thereby lubricating the pressure adjusting mechanism 31 even when the operation is stopped. Since the supply path of the oil 41 is always blocked by either the opening 50 of the liquid escape path 104 or the supply restriction unit 101, excessive supply of the lubricating oil 41 or take-out to the outside is possible even if the differential pressure oil supply system is adopted. Does not occur. Therefore, a check valve is not necessary.
[0042]
The scroll compressor of the example shown in FIGS. 1 and 2 will be described more specifically. The compression mechanism unit 2 is arranged vertically in the container 1 together with the electric motor 3. The electric motor 3 includes a stator 4 fixed inside the container 1 and a rotor 5 positioned inside the stator 4, and a crankshaft 6 is coupled to the rotor 5 in a penetrating state. One end side of the crankshaft 6 is supported via a main bearing 8 by a main bearing member 7 which is a support member constituting a part of the compression mechanism portion 2. The main bearing member 7 is fixed in the container 1, and the swirl swirl component 11 is accommodated between the main swirl member 10 and the fixed swirl component 10 attached thereto, and is held in a state of meshing with the fixed swirl component 10. As the rotation restraining means for preventing the rotation of the swirl spiral part 11 between the main bearing member 7 and the swirl spiral part 11 and moving in a circular orbit, the rotation restraint part 12 such as an Oldham ring or a mechanism is used. A swirl spiral part 11 is driven via a swivel bearing 13 by an eccentric part 9 that performs an eccentric motion with respect to the crankshaft 6 provided at the tip of one end protruding on the bearing 8, and the swirl swirl part 11 is fixed to the fixed swirl part. By making only the swivel motion with respect to 10, the compression space 32 is moved from the outer periphery toward the center of the spiral while reducing the volume, for example, refrigerant gas or the like is sucked from the external cycle through the suction port 14 and compressed. . The compressed refrigerant gas or the like passes through the discharge port 15 and is discharged into the container inner space 16.
[0043]
Further, the other end side of the crankshaft 6 is supported by a sub bearing 17a of a sub bearing member 17 which is a support member fixed in the container 1. A positive displacement pump 18 is provided at the tip of the crankshaft 6 that protrudes downward from the auxiliary bearing 17a on the other end side. The volume pump 18 is driven together with the compression mechanism portion 2 by the crankshaft 6, and the lubricating oil 41 stored in the liquid reservoir portion 19 is disposed on the upper portion of the eccentric portion 9 through an oil supply path 20 provided in the axial direction at the center of the crankshaft 6. The liquid is supplied to the liquid reservoir 21. The lubricating oil 41 supplied to the liquid reservoir 21 lubricates and cools the slewing bearing 13, lubricates the main bearing 8 through the next liquid reservoir 22, and then returns to the liquid reservoir 19 and is recirculated.
[0044]
On the other hand, a part of the lubricating oil 41 supplied to the liquid reservoir 21 passes through the elongated hole 23 provided inside the swirl spiral component 11 and is connected to the swivel end plate 25 and the main through the narrowed portion 24 formed by a narrow throttling hole. The pressure is reduced and supplied to a back pressure chamber 29 surrounded by a recess 26 provided in the bearing member 7, a surface 27 of the fixed spiral component 10, and a seal member 28. Here, the back pressure chamber 29 has a lower pressure than the liquid reservoirs 21 and 22. Therefore, the sealing member 28 has a role of sealing between the liquid reservoirs 21 and 22 which are high pressure portions and the back pressure chamber 29 having a pressure lower than that, and preventing communication between them without passing through the throttle portion 24. Yes. The rotation restraint component 12 is disposed in the back pressure chamber 29 and is lubricated by the lubricating oil 41 supplied to the back pressure chamber 29.
[0045]
As the lubricating oil 41 supplied to the back pressure chamber 29 accumulates, the pressure in the back pressure chamber 29 rises and causes excessive contact between the fixed and swirl spiral components 10 and 11. Therefore, in order to keep the pressure within a certain range, the pressure adjusting mechanism 31 is provided between the back pressure chamber 29 and the suction region 30 which is the low pressure region of the compression space 32. The pressure adjusting mechanism 31 is activated when the pressure in the back pressure chamber 29 becomes higher than the set pressure, and opens the liquid escape path 104 to allow excess lubricating oil 41 in the back pressure chamber 29 to escape to the suction area 30 to be compressed. Supply to the space 32. As a result, the pressure in the back pressure chamber 29 is kept substantially constant, and the lubricating oil 41 supplied to the suction area 30 is guided to the compression space 32, and serves as a seal that prevents leakage of refrigerant gas and the like during compression, It plays a role of lubricating the contact surface between the fixed spiral component 10 and the swirl spiral component 11.
[0046]
In addition, the lubricating oil 41 supplied to the liquid reservoir 21 has the first passage 36 and the concave portion 38 formed on the sliding surface of the swirl swirl component 11 of the fixed swirl component 10 with the swirl swirl component 11. 2A is supplied to and stored in the recess 38 through the first passage 36, and is temporarily confined after the connection is cut off. Next, the swirl spiral component 11 is accumulated along with the swivel motion. After that, as shown in FIG. 2B, the lubricating oil 41 stored in the concave portion 38 is stored in the second passage 37 when the concave portion 38 communicates with the second passage 37 as shown in FIG. Is supplied to the holding groove 34 of the tip seal 33 formed at the tip of the blade of the swirl spiral component 11.
[0047]
As described above, the lubricating oil 41 supplied from the liquid reservoir 19 to the liquid reservoir 21 above the eccentric portion 9 of the crankshaft 6 by the positive displacement pump 18 is held by the first passage 36 and the second passage 37. An appropriate amount of lubricating oil 41 is supplied to the entire compression space 32 from the discharge port 15 to the suction port 14 intermittently supplied to the space formed by the gap on the back surface of the chip seal 33 in the groove 34. Further, the amount of the lubricating oil 41 supplied to the bottom surface of the holding groove 34 can be easily controlled by the volume of the accumulation space formed by the recess 38 provided in the fixed spiral component 10. Therefore, it is possible to prevent performance degradation due to suction heating that occurs when a large amount of high-pressure lubricating oil 41 flows into the low-pressure suction area 30 side in the compression space 32, and a scroll compressor with high performance and reliability can be realized. .
[0048]
However, the lubricating oil 41 in the concave portion 38 has the same pressure as the lubricating oil 41 in the liquid reservoir 21, and when the concave portion 38 communicates with the holding groove 34, the lubricating oil 41 is supplied due to a difference with the pressure on the holding groove 34 side. Accordingly, the lubricating oil 41 remains in the recess 38.
[0049]
The scroll compressor of the example shown in FIG. 3 employs a supply restriction unit 101 that uses the throttle unit 24 and the intermittent communication unit 103 described above in addition to the intermittent supply mechanism 100 of the examples of FIGS. is there. As shown in FIGS. 4A to 4D, the relationship between the throttle hole opening 24a of the throttle portion 24 and the seal member 28 at the turning position of the swirl spiral component 11 at every 90 ° is shown. 24 a performs a circular motion while straddling the seal member 28 between the liquid reservoir 22 and the back pressure chamber 29. When the throttle hole opening 24 a faces the seal member 28 or the liquid reservoir 22, the lubricating oil 41 is not supplied to the back pressure chamber 29. On the other hand, when the throttle hole opening 24 a faces the back pressure chamber 29, the lubricating oil 41 in the liquid reservoir 22 is supplied to the back pressure chamber 29 through the long hole 23 and the throttle portion 24. Therefore, if the time ratio of the throttle hole opening 24a facing the back pressure chamber 29 is changed in design, the supply amount of the lubricating oil 41 to the back pressure chamber 29 can be adjusted. In this case, the throttle hole opening 24a can change the design of the diameter of the trajectory when the circular movement is performed by setting the formation position, and can adjust the time ratio facing the back pressure chamber 29. There is no problem as in the case where the diameter of the aperture hole of 24 is reduced and the length is increased.
[0050]
Instead of supplying the lubricating oil 41 to the back pressure chamber 29 through the long hole 23, the throttle portion 24 intermittently communicates with the back pressure chamber 29. Of course, the same effect can be obtained by using a configuration in which lubricating oil is supplied to the back pressure chamber 29 through the long hole 23. Thereby, in addition to the operation shown in FIGS. 1 and 2, lubricating oil adjusted to an appropriate amount can be supplied to the compression chamber near the suction hole, and a high-performance and low-cost scroll compressor can be realized.
[0051]
The scroll compressor of the example shown in FIG. 5 branches the supply restriction unit 101 having the throttle unit 24 and the intermittent communication unit 103 of the example of FIG. 4 from the middle of the first passage 36 in the intermittent supply mechanism 100 described above. And formed. By doing so, the number of processing steps can be reduced and realized, and this advantage is the same even when any one of the throttle portion 24 and the intermittent communication portion 103 is provided.
[0052]
The scroll compressor of the example shown in FIGS. 6 and 7 includes lubricating oil 41 from the liquid reservoir 19 of the example of FIG. 3 to the back pressure chamber 29 and the holding groove 34 of the tip seal 33 in the swirling spiral component 11 through the crankshaft 6. The lubricating oil 41 supplied to the oil supply path 20 lubricates the main bearing 8, cools and lubricates the swivel bearing 13 through the rear liquid reservoir 22, reaches the liquid reservoir 21, and intermittently from here. Intermittent supply to the holding groove 34 via the supply mechanism 100 is performed, and intermittent supply from the liquid reservoir 22 to the back pressure chamber 29 via the supply restricting portion 101 having the throttle portion 24 and the intermittent communication portion 103 is performed. In addition, a pressure adjusting mechanism 31 is provided in the liquid escape path 104 from the back pressure chamber 29 described above to the low pressure suction area 30 of the compression space 32, and the opening 50 of the liquid escape path 104 is a swirl spiral. parts To the back pressure chamber 29 with the first pivot is obtained so as to communicate intermittently. Accordingly, the intermittent supply mechanism 100 described in the example of FIG. 1, the supply restriction unit 101 having the throttle unit 24 and the intermittent communication unit 103 described in the example of FIG. 3, and the pressure already described with reference to FIGS. The features of each of the adjustment mechanisms 31 are exhibited. Other configurations are not particularly different from the example shown in FIG. Accordingly, common members are denoted by the same reference numerals, and redundant description is omitted.
[0053]
Even if the liquid supply mechanism 102 of this example is of a differential pressure oil supply system, the intermittent communication portion 103 in the supply restricting portion 101 exceeds the outside of the seal member 28 as shown in FIG. When the operation is stopped in a state in which the first and second passages 36 and 37 are communicated with each other, the first and second passages 36 and 37 of the intermittent supply mechanism 100 are not communicated. No take-out to At the same time, since the opening 50 of the liquid escape path 104 of the pressure adjusting mechanism 31 is blocked by the swivel end plate 25, the lubricating oil 41 is not supplied from the back pressure chamber 29 to the suction area 30. Does not occur.
[0054]
Further, as shown in FIG. 7B, even when the operation is stopped in a state where the opening 50 of the liquid escape path 104 of the pressure adjusting mechanism 31 communicates with the back pressure chamber 29, the intermittent communication unit 103 in the supply restriction unit 101. Is located on the inner side of the seal member 28 and does not communicate with the back pressure chamber 29, the lubricating oil 41 in the back pressure chamber 29 is not supplied to the suction area 30 via the pressure adjustment mechanism 31, and excessive supply or No external take-out occurs. Since the first and second passages 36 and 37 of the intermittent supply mechanism 100 are not communicated, the supply of the lubricating oil 41 to the holding groove 34 is not performed, and excessive supply or take-out to the outside does not occur.
[0055]
【The invention's effect】
Scroll compression of the present invention In machine According to the swirl swirl component, the suction, compression, and discharge operations are repeated by swirling the swirl swirl component. By supplying liquid to the back side of the swivel part and the holding groove of the sealing member at the blade tip of the swirl swirl part, the swirl swirl part is backed up by the back pressure of the supplied liquid on the back side of the outer periphery of the swirl swirl part At the same time, the supply of liquid is performed based on specified restrictions, so that there is no excess or deficiency of backup, and a stable swivel operation that does not leave the fixed spiral part and does not contact excessively is ensured. Compressive performance and durability can be improved by sealing and lubricating between the swirling spiral parts. In particular, the supply of liquid to the holding groove is restricted by the high pressure of the liquid pool and the supply to the back pressure chamber during intermittent direct or indirect communication between the liquid pool and the holding groove associated with the swirling swirl part. By supplying the liquid in an environment where excess liquid is likely to be generated without squeezing it, it is easy to reach the high pressure area of the holding groove, but as a whole, the ratio of the time between the liquid pool and the holding groove Since the amount of liquid to be supplied is regulated by setting the flow rate, an appropriate amount of liquid is supplied to the entire area including the high-pressure area of the holding groove while suppressing the outflow to the low-pressure suction area. A moving compressor can be lubricated, and a scroll compressor with high performance and reliability is realized.
[0056]
In particular The supply to the holding groove supplies the liquid in the liquid reservoir to the concave portion when the first passage leads to the concave portion as the swirling spiral component turns, and the concave portion has a different timing from the first passage, and therefore the first passage. Since the liquid in the recess communicates with the second passage at the timing when it does not communicate with the first passage, the liquid in the recess is supplied to the holding groove. The amount of liquid that is easy to spread even in the high-pressure region of the holding groove in the environment is reliably regulated by a recess that does not pass through the first and second passages without being squeezed. It is possible to supply an appropriate amount of liquid to the entire compression space while suppressing outflow to the suction area side, and to achieve sealing and lubrication. A scroll compressor with high performance and reliability is indispensable. And offer as cheap It is possible. Further, even if the differential pressure oil supply method is adopted, one of the first and second passages is closed between the recesses and does not communicate with each other, so that the liquid continues to be supplied by the differential pressure remaining when the operation is stopped. There is no such thing as an excess supply of liquid and no take-out to the outside. Therefore, a check valve is not necessary.
[0057]
However, even if the first and second passages are intermittently communicated through the recess, there is no problem as long as the oil supply method uses a positive displacement pump, and even if intermittently communicated, the supplied liquid is regulated to an appropriate amount. However, it is possible to make it easy to supply the high pressure part by using the entire supply pressure when communicating.
[0058]
Further, the supply restricting portion of the liquid supply mechanism may be configured such that the swirl part of the swirling spiral component is provided in a passage provided with a passage for supplying liquid from the liquid reservoir to the back pressure chamber, or a passage having or not having the restriction portion. Any intermittent communication part may be used as long as it is intermittently communicated with the movement. In the latter case, in particular, it can be limited in any way by setting the time ratio and flow rate intermittently associated with the swirling of the swirling spiral part. Even when the supply restriction is increased to prevent excessive pressure and suction heating, the problem is that the diameter and diameter of the throttle hole are reduced or lengthened as before, and clogging is likely to cause clogging and performance and reliability are difficult. All of the problems of high cost are solved, and a scroll compressor with higher efficiency and lower cost is realized. In addition, by combining the throttle part, the throttle part is easy to process and does not cause clogging.Therefore, higher supply restriction can be suppressed to suppress pulsating flow due to intermittent supply without particularly increasing the cost. However, it can be easily achieved, and further stability of performance and further prevention of inhalation heating can be achieved.
[0059]
In the case where the supply restricting portion is intermittently connected to the passage, if the time for communication is set to be different from the time for the concave portion to communicate with the first passage, the supply pressure of the liquid to the concave portion is reduced. It is not lowered by the liquid supply for the pressure, and it becomes easier to ensure the supply of the liquid to the high pressure region of the holding groove.
[0060]
In addition, when the supply restricting portion is provided in the branch passage branched from the middle of the first passage, since the portion of the first passage is provided in common, the passage structure is simple and easy to process. Cost is further reduced.
[0061]
Equipped with a pressure adjustment mechanism that allows excess liquid in the back pressure chamber to escape through the path and maintain the back pressure chamber at a predetermined pressure, and the escape path has an opening that intermittently leads to the back pressure chamber as the swirl swirl part turns. In the configuration, the back pressure is adjusted by a simple method that allows excess liquid to escape and escape through the path to maintain a more appropriate back pressure state. Is supplied to the compression space by the differential pressure method and used for sealing and lubrication there, so that the sealing and lubrication functions between the fixed and swirling spiral parts are further improved. Moreover, since the opening of the escape path is intermittently communicated with the back pressure chamber as the swirl swirl part swivels, it is not possible to supply the relieved liquid to the suction area for back pressure adjustment, and there is a problem of suction heating. It can be suppressed from occurring. In particular, by making the time for the opening of the escape path intermittently communicated with the back pressure chamber different from the time for intermittently communicating with the supply restricting section, the liquid passage to the pressure adjustment mechanism can be relieved even if the operation is stopped. Since it is always shut off at either the opening or the supply restricting portion, even if the differential pressure oil supply method is adopted, excessive supply of liquid or take-out to the outside does not occur. Therefore, a check valve is not necessary.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing one example of a scroll compressor according to an embodiment of the present invention.
2 is a partial cross-sectional view showing two operating states (a) and (b) of the compression mechanism of the scroll compressor of FIG. 1;
FIG. 3 is a partial cross-sectional view of a compression mechanism showing another example of the scroll compressor according to the embodiment of the present invention.
4 is a rear view of swirl spiral parts in the scroll compressor of FIG. 3 viewed at swivel positions (a) to (d) every 90 °. FIG.
FIG. 5 is a partial cross-sectional view of a compression mechanism showing another example of the scroll compressor according to the embodiment of the present invention.
FIG. 6 is a sectional view showing another example of the scroll compressor according to the embodiment of the present invention.
7 is a partial cross-sectional view showing a compression mechanism in the scroll compressor of FIG. 6 in two operating states (a) and (b).
FIG. 8 is a cross-sectional view showing one example of a conventional scroll compressor.
9 is a cross-sectional view of a throttle portion of a lubricating oil supply path in the scroll compressor of FIG.
FIG. 10 is a cross-sectional view showing another example of a conventional scroll compressor.
11 is an enlarged cross-sectional view of the scroll compressor of FIG. 10 when the check valve is stopped.
12 is an enlarged cross-sectional view of the scroll compressor of FIG. 10 during operation of a check valve.
[Explanation of symbols]
1 container
2 Compression mechanism
3 Electric motor
6 Crankshaft
8 Main bearing
9 Eccentric part
10 Fixed spiral parts
11 Swirling spiral parts
13 Slewing bearing
14 Suction port
15 Discharge port
16 Space inside the container
17a Secondary bearing
19 Liquid reservoir
20 Refueling route
21, 22 Liquid pool
23 Long hole
24 Aperture
10a, 25 Rotating end plate
28 Seal member
29 Back pressure chamber
30 Inhalation area
31 Pressure adjustment mechanism
32 compression space
33 Tip seal
34 Holding groove
36 First passage
37 Second passage
38 recess
50 openings
100 Intermittent supply mechanism
101 Supply restriction unit
102 Liquid supply mechanism
103 Intermittent communication
104 Fluid escape route

Claims (4)

The fixed spiral part and the swirl spiral part, whose blades rise from the end plate, are meshed with each other to form a compression space between them, and when the swirl spiral part is circularly orbited with respect to the fixed spiral part, the compression space moves and the volume is increased. The fluid supplied to the liquid reservoir on the back of the swirl swirl part as the swirl drive of the swirl swirl part is changed to the back of the back side of the outer periphery of the swirl swirl part. In addition to being supplied to the pressure chamber through the swirl swirl part through the swirl swirl part, the liquid is passed through the swirl swirl part to the holding groove that holds the seal member between the swirl swirl part blade and the fixed swirl part at the tip. In a scroll compressor having a liquid supply mechanism for supplying,
The liquid supply mechanism includes a concave portion provided on a surface that slides with the swirl spiral component of the fixed swirl component, and a liquid swirl component that is provided in the swirl spiral component and intermittently communicates with the concave portion as the swirl spiral component rotates. A first passage to be supplied to the recess, and a second passage provided in the swirl spiral component and supplying the liquid in the recess to the holding groove through the recess at a timing different from that of the first passage. A scroll compressor comprising a passage.   The supply restricting portion of the liquid supply mechanism is a throttle portion provided in a passage for supplying liquid from the liquid reservoir to a back pressure chamber, or a passage having or not having the throttle portion is used for a swiveling motion of the swirling spiral component. The scroll compressor according to claim 1, wherein the scroll compressor is an intermittent communication portion that is intermittently communicated.   The scroll compressor according to claim 2, wherein the supply restriction unit is provided in a branch passage branched from the middle of the first passage.   A pressure adjusting mechanism is provided to allow excess liquid in the back pressure chamber to escape through the path and maintain the back pressure chamber at a predetermined pressure, and the relief path has an opening that intermittently communicates with the back pressure chamber as the swirl swirl component swivels. The scroll compressor according to any one of claims 1 to 3.

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