JP5168191B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor used for an air conditioner, a refrigerator, a blower, a water heater, and the like.

  In a general scroll compressor, a plurality of compression chambers are formed by meshing a fixed scroll having a spiral wrap formed on an end plate and a turning scroll, and a crankshaft having an eccentric portion is connected to the turning scroll. Such a scroll compressor performs compression while reducing the volume toward the center by using an Oldham ring to prevent rotation and to make a turning motion. In a scroll compressor, the oil mixed with the working fluid in the compression chamber helps reduce sliding loss and wear due to lubrication of the contact surface between the fixed scroll and the orbiting scroll, and prevents seizure. It also contributes to the reduction of leakage loss by filling the seal part and improving the sealing performance.

  However, when the oil is supplied from the vicinity of the suction, the scroll compressor causes suction overheating and the capacity is reduced. Therefore, a method of directly supplying the oil to the compression chamber during the compression is often employed.

  Therefore, in the scroll compressor of Patent Document 1 shown in FIG. 11, the oil supply hole 102 is provided in the lap upper surface 101a of the orbiting scroll 101, and the outer periphery of the orbiting scroll wrap outer wall 101b and the inner wall 101c are communicated around the opening. Directional grooves 103 are provided. Thus, in this scroll compressor, a necessary and sufficient amount of oil is contained in both the compression chambers of the first compression chamber formed on the side of the orbiting scroll wrap outer wall 101b and the second compression chamber formed on the side of the inner wall of the orbiting scroll wrap 101c. Is supplied.

  Although this configuration has an advantage that oil supply can be performed by a very simple process, the pressures of the first compression chamber and the second compression chamber are different while the circumferential groove 103 faces, so both compressions are performed. The amount of oil supplied to the chambers becomes uneven, one of the compression chambers causes excessive oil loss and viscosity loss, and the other compression chamber causes insufficient oil loss and wear, resulting in proper oil supply to both compression chambers. There is a problem that it is difficult.

  As a countermeasure, in the scroll compressor of Patent Document 2 shown in FIG. 12, the end plate 201a of the fixed scroll 201 is provided with an oil supply hole 204 that can be opened in both the first compression chamber 202 and the second compression chamber 203. The opening time to the second compression chamber 203 is set longer than the opening time to the first compression chamber 202.

That is, the pressure in the compression chambers 202 and 203 facing the oil supply hole 204 is always higher in the second compression chamber 203 and the amount of oil supply per unit time is smaller in the second compression chamber 203. By extending the opening time accordingly, an equal amount of oil is supplied to both compression chambers 202 and 203.
JP 2005-139997 A Japanese Patent Laid-Open No. 3-88888

  In the conventional configuration of Patent Document 1 described above, in the symmetrical scroll in which the confining volume of the first compression chamber and the confining volume of the second compression chamber are equal, the sections supplied from the oil supply holes are the first compression chamber and the second compression chamber. Therefore, the amount of oil supplied to the first compression chamber that opens earlier after closing is greater than the amount of oil supplied to the second compression chamber.

  On the other hand, even in an asymmetric scroll in which the confining volume of the first compression chamber is larger than the confining volume of the second compression chamber, the pressure increase rate of the second compression chamber is larger than the pressure increase rate of the first compression chamber. The pressure in the first compression chamber during refueling becomes smaller than the pressure in the second compression chamber, and the amount of oil in the first compression chamber becomes larger than the amount of oil in the second compression chamber, as in the case of the symmetrical scroll.

  That is, regardless of the scroll shape, the amount of oil supplied to the first compression chamber is larger than the amount of oil supplied to the second compression chamber and is generally uneven, so that the first compression chamber is excessively oily and the second compression chamber. Is prone to oil shortage.

  In addition, although the conventional configuration of Patent Document 2 has a substantially equal amount of oil supplied to the first compression chamber and the second compression chamber, the ratio of the time during which one compression chamber is open to both compression chambers is large. There is a problem that the amount of oil supply tends to be excessive, and mechanical loss due to oil viscosity increases.

  Further, in order to reduce the amount of oil supply per rotation to an appropriate amount, it is necessary to make the oil supply hole very small and provide a throttle, but there remains a problem in workability.

  The present invention solves the above-mentioned conventional problems, and can supply the minimum necessary amount of oil, realize reduction of sliding loss and leakage loss, prevention of wear and seizure, An object is to provide a highly efficient and highly reliable scroll compressor capable of suppressing an increase in viscosity loss due to excessive oil supply.

In order to solve the above-described conventional problems, the present invention has a spiral scroll scroll and a orbiting scroll lap that mesh with each other to form at least a first compression chamber and a second compression chamber between the scrolls. , The first compression chamber on the outer wall side of the orbiting scroll wrap and the second compression chamber on the inner wall side of the orbiting scroll wrap are directed to the scroll compressor in which the volume changes. Oil supply holes are formed on the upper surface of at least one lap, a first oil supply passage connecting the opening of the oil supply hole and the first compression chamber, and a second oil supply passage connecting the opening of the oil supply hole and the second compression chamber, It is formed on the upper surface of the lap in which the oil supply holes are formed, and the outlets of the first oil supply passage and the second oil supply passage are different from each other on the lap in which the oil supply holes are formed. Provided at a position of the opening angle, the volume ratio of the first compression chamber when said first oil supply passage starts to open to the first compression chamber, the second oil supply passage starts to open to the second compression chamber It is more than the volume ratio of the said 2nd compression chamber at the time .

  In the conventional configuration, the oil viscosity loss increases due to an excessive amount of oil supply, leading to a reduction in efficiency. According to this configuration, the first oil supply passage and the second oil supply passage act as a throttle for oil supply, and the minimum required A limited and appropriate amount of oil can be evenly supplied to the first compression chamber and the second compression chamber, reducing sliding loss and leakage loss, preventing wear and seizure, and viscosity due to excessive oil supply It is also possible to suppress an increase in loss. As a result, a highly reliable scroll compressor can be realized.

In the first invention, the volume ratio of the first compression chamber when the first oil supply passage starts to open to the first compression chamber is the same as that of the second compression chamber when the second oil supply passage starts to open to the second compression chamber. By setting it to a volume ratio or higher, the pressure in both compression chambers is approximately the same while both oil supply passages are open to both compression chambers, so an equal amount of oil is supplied to both compression chambers with one oil supply hole. It is possible.

A second invention is, in particular, in the scroll compressor of the first invention, by volume confinement of the first compression chamber is greater asymmetric scroll than the volume confinement of the second compression chamber, from the inlet port The distance of the fluid passage until compression is started, that is, the length of the suction chamber is shorter than that of the symmetric scroll, thereby suppressing a decrease in volume efficiency due to a suction heating phenomenon in which the working fluid receives heat from a high temperature fixed scroll. The efficiency of the compressor can be increased.

In the third aspect of the invention, in particular, in the scroll compressor of the first or second aspect of the invention, the length of the second oil supply passage is longer than the length of the first oil supply passage. In both the symmetric scroll and the asymmetric scroll, the pressure in both compression chambers tends to be higher in the second compression chamber while both oil supply passages are open to both compression chambers. When return or oil compression occurs, the phenomenon in which the pressure in the compression chamber becomes considerably larger than the discharge pressure is more likely to occur in the second compression chamber, and oil or working fluid flows backward through the second oil supply passage and oil supply hole. Reliability may be impaired due to lack of oil or temperature rise. Therefore, by adopting the configuration of the third aspect of the invention, it is possible to secure the distance from the second compression chamber to the oil supply hole and suppress the above-mentioned risk.

The fourth aspect of the invention is particularly the scroll compressor according to any one of the first to third aspects of the invention, wherein the oil supply hole and the oil supply passage are provided in the orbiting scroll lap, and in particular, to the compression mechanism portion via the crankshaft. In a compressor having a configuration in which oil is supplied, an oil supply path from an oil reservoir below the compressor to an oil supply hole provided in the orbiting scroll wrap can be easily configured.

In a fifth aspect of the invention, in particular, in the scroll compressor according to any one of the first to third aspects, the orbiting scroll is pressed against the fixed scroll to perform a compression operation, and an oil supply hole and an oil supply passage are provided in the fixed scroll wrap. This reduces the loss of leakage by pressing the orbiting scroll against the fixed scroll, and at the same time, directly lubricates the top surface of the fixed scroll that receives the load of the orbiting scroll, improving the lubricity of this thrust sliding surface and reducing the sliding loss. It is possible to achieve reduction of wear, suppression of wear and seizure.

  Further, in a compressor having a structure in which the compression mechanism part is partially or entirely immersed in an oil reservoir below the compressor, an oil supply path from the oil reservoir to the oil supply hole provided in the fixed scroll wrap can be easily configured. You can also. However, in a compressor in which the compression mechanism section is immersed in oil, the amount of heat transferred from the hot oil in the oil reservoir to the compression mechanism section is very large, causing suction overheating, so the compression mechanism section is immersed in oil. Volume efficiency is slightly inferior compared to no compressor.

  In the case of a horizontal scroll compressor, either a configuration in which oil is supplied to the compression mechanism portion via a crankshaft or a configuration in which oil is supplied from a fixed scroll partially immersed in an oil reservoir can be used. Either of the scrolls may be provided with an oil supply hole or both. Further, the bearing portion of the crankshaft, the Oldham ring sliding portion, and the like may be supplied with oil via the crankshaft, and the oil supply to the compression chamber may be performed through an oil supply hole provided in the fixed scroll.

In the sixth aspect of the invention, in particular, in the scroll compressor according to any one of the first to fifth aspects, carbon dioxide is used as the working fluid. Carbon dioxide refrigerant is suitable for heat pump water heaters because it is advantageous for high temperature difference heating, and the discharge temperature of the compressor is set to a very high temperature of 90 ° C. or higher in order to secure a high temperature hot water temperature of 80 ° C. or higher. Since it is necessary to set, the temperature of the compression mechanism is very high. In addition, since carbon dioxide is a high-pressure refrigerant, the load applied to each component of the compression mechanism is very high.

  As described above, the configuration of the present invention is particularly effective in order to ensure high efficiency and reliability in the vicinity of the compression mechanism, particularly in the vicinity of the compression chamber, in a high temperature and high load operation state.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention.

  In FIG. 1, the entire inside of the iron hermetic container 1 becomes a high-pressure atmosphere communicating with the discharge pipe 2. An electric motor 3 is disposed at a substantially central portion of the hermetic container 1, and a compression mechanism is disposed above the electric motor 3. A main body frame 5 of a compression mechanism that supports one end of a crankshaft 4 fixed to the rotor 3 a of the electric motor 3 is fixed to the sealed container 1, and a fixed scroll 6 is attached to the main body frame 5.

  One end of the axial oil passage 7 provided in the crankshaft 4 communicates with the oil supply pump device 8 and the other end finally communicates with the eccentric bearing 10 of the orbiting scroll 9. The orbiting scroll 9 that meshes with the fixed scroll 6 to form at least two compression chambers 11 is composed of an orbiting end scroll 9b in which a spiral orbiting scroll wrap 9a and an eccentric bearing 10 are upright, and the fixed scroll 6 and the main body frame. 5 is arranged. In FIG. 1, for convenience of illustration, only one compression chamber is provided with a reference number 11.

  The fixed scroll 6 includes a fixed end plate 6a and a spiral fixed scroll wrap 6b. A discharge port 12 and a discharge chamber 13 communicating with the discharge port 12 are provided in the central portion of the fixed scroll wrap 6b, and a suction chamber serving as a working fluid passage until compression starts in the outer peripheral portion thereof. 15 is arranged. Here, carbon dioxide is an example of the working fluid.

  An eccentric shaft 16 that is eccentric from the main shaft of the crankshaft 4 and is disposed at the upper end of the crankshaft 4 engages and slides with the eccentric bearing 10 of the orbiting scroll 9. A minute gap is provided between the back surface 9c of the orbiting end plate 9b and the thrust restraining surface 5a provided on the main body frame 5 that restricts the movement of the orbiting scroll 9 in the axial direction. An annular seal member 17 is mounted in a loose state on the thrust restraining surface 5a of the main body frame 5, and the annular seal member 17 partitions an inner back chamber 18 and an outer back pressure chamber 19 from each other.

  The oil sucked up by the oil supply pump device 8 passes through the oil passage 7 of the crankshaft 4 and is guided to the axial inner space 20 formed between the eccentric bearing 10 and the eccentric shaft 16 of the orbiting scroll 9. Part of the guided oil leads to a back pressure chamber 19 formed by being surrounded by the fixed scroll 6 and the main body frame 5 via a throttle portion 21 provided on the revolving end plate back surface 9 c of the revolving scroll 9. The revolving scroll 9 is guided to the suction chamber 15 through the back pressure adjusting valve 22 having the function of pressing the orbiting scroll 9 against the fixed scroll wrap 6b and the oil supply passage 22a. On the other hand, other oil passes through the eccentric bearing 10, the back chamber 18 and the main bearing 23 and is discharged to the outside of the compression mechanism.

  A check valve device 24 for opening and closing the outlet side of the discharge port 12 is mounted on the plane of the fixed end plate 6a of the fixed scroll 6. The check valve device 24 includes a reed valve 24a made of a thin steel plate, a valve presser 24b, Consists of.

  The lower end of the crankshaft 4 is supported by a secondary bearing 25 fixed by welding or shrink fitting in the sealed container 1 and can rotate stably. The auxiliary bearing 25 has a journal bearing structure, for example, and a part of the oil sucked up by the oil supply pump device 8 is supplied to the auxiliary bearing 25.

  The gas immediately after being compressed and discharged from the discharge port 12 by the compression mechanism and the gas immediately before being discharged from the discharge pipe 2 are partitioned by the muffler 26, and the gas immediately after being discharged from the discharge port 12 is the muffler 26. Is passed through a downward gas passage 27 provided in the vicinity of the outer periphery of the compression mechanism, and is guided to the upper portion of the rotor 3a as shown by the dotted arrow in the figure. Here, the main bearing 23 and the like are joined with the oil discharged after lubrication, and after reaching the lower part of the rotor 3a through the rotor passage 3b provided in the rotor 3a, the mixed flow of gas and oil is centrifuged. It collides with the lower coil end of the stator 3c by force, and gas-liquid separation occurs. The gas after gas-liquid separation is guided to the upper part of the electric motor 3 through a stator passage 3d provided on the outer periphery of the stator 3c, and passes through an upward gas passage (not shown) provided in the compression mechanism. After reaching the upper space, the liquid is discharged from the discharge pipe 2 to the outside of the closed container 1.

  FIG. 2 is a front view of an example of the orbiting scroll 9 shown in FIG. 1, and FIG. 3 is a view of the orbiting scroll 9 viewed from the back 9c side by combining the orbiting scroll 9 shown in FIG. 2 and the fixed scroll 6 shown in FIG. It is a figure. As shown in FIGS. 1 to 3, the orbiting scroll wrap 9 a is provided with an oil supply hole 28 along the height direction thereof, and communicates with the internal space 20 of the eccentric bearing 10 that is substantially the discharge pressure. On the upper surface 9d of the orbiting scroll wrap 9a, an upper surface groove 29 including the opening of the oil supply hole 28 is provided in the extending direction of the orbiting scroll wrap 9a. The orbiting scroll wrap outer wall 9e and the fixed scroll wrap inner wall 6c form a first compression chamber 11a, which is one of the compression chambers 11. The orbiting scroll wrap inner wall 9f and the fixed scroll wrap outer wall 6d One second compression chamber 11b is formed. At both ends of the upper surface groove 29, a first oil supply passage outlet 30a that communicates with the first compression chamber 11a and a second oil supply passage outlet 30b that communicates with the second compression chamber 11b are provided. Here, the outlet 30a and the outlet 30b are provided at different extension angles on the upper surface 9d.

  About the scroll compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  The high-pressure oil guided from the internal space 20 of the orbiting scroll 9 to the oil supply hole 28 is supplied to the first compression chamber 11a while being decompressed through the first oil supply passage between the oil supply hole 28 and the first oil supply passage outlet 30a. Is done. Similarly, the oil reduced in pressure through the second oil supply passage between the oil supply hole 28 and the second oil supply passage outlet 30b is supplied to the second compression chamber 11b. The amount of oil supplied to the compression chambers 11a and 11b at this time is generally determined by the pressure in the compression chambers 11a and 11b while the oil supply passage outlets 30a and 30b are facing the compression chambers 11a and 11b.

  FIG. 4 is a graph of the pressure change from the closing of both the compression chambers 11a and 11b to the discharge in the case of a symmetrical scroll in which the first compression chamber 11a and the second compression chamber 11b have the same closed volume. The axis indicates the crank angle. For the first compression chamber 11a and the second compression chamber 11b, the crank angle and the pressure are substantially equal. The first oil supply passage outlet 30a opens to the first compression chamber 11a during the crank angle θ11 to θ12, and the pressure in the first compression chamber 11a at that time increases from P11 to P12. Similarly, the second oil supply passage outlet 30b opens to the second compression chamber 11b having pressures P21 to P22 between the crank angles θ21 to θ22. (Θ12−θ11) and (θ22−θ21) are approximately 360 degrees in any configuration.

FIG. 5 is a graph showing the pressure change and the opening timing of the circumferential groove 103 in the case of the symmetric scroll in the conventional configuration shown in FIG.
The crank angle θ11 at which the circumferential groove 103 opens in the first compression chamber on the b side is approximately 180 degrees earlier than the crank angle θ21 opened in the second compression chamber on the orbiting scroll wrap inner wall 101c side, and the pressure in the opening is One compression chamber is smaller. Therefore, there is a problem that the first compression chamber has a larger amount of oil supply than the second compression chamber, the first compression chamber has increased viscosity loss due to excessive oil supply, and the second compression chamber has increased leakage loss due to insufficient oil supply. There is a problem that it occurs simultaneously and it is difficult to optimize the total amount of oil supplied from the oil supply hole 102.

  On the other hand, in the example shown in FIG. 4, by setting the opening start of the second oil supply passage outlet 30b to be the same as or earlier than the opening start of the first oil supply passage outlet 30a, the pressures of both the compression chambers 11a and 11b are generally set. As an equivalent, both the compression chambers 11a and 11b can be evenly refueled. Therefore, by optimizing the total amount of oil supplied from the oil supply holes 28, the necessary and sufficient amount of oil that does not cause wear or seizure is reduced while minimizing the viscosity loss and leakage loss of both the compression chambers 11a and 11b. It is possible to realize.

  FIG. 6 is a graph of the pressure change from the closing of the compression chambers 11a and 11b to the discharge in the case of an asymmetric scroll in which the confining volume of the first compression chamber 11a is larger than the confining volume of the second compression chamber 11b. The horizontal axis of this graph indicates the crank angle. The first compression chamber 11a starts compression from a crank angle that is 180 degrees earlier than the second compression chamber 11b, and the pressure increase speed of the second compression chamber 11b is larger. As in FIG. 4, the opening crank angle of the first oil supply passage outlet 30a is θ11 to θ12, and the pressure in the first compression chamber 11a at that time increases from P11 to P12. The opening crank angle of the second oil supply passage outlet 30b is θ21 to θ22, and the pressure in the second compression chamber 11b at that time increases from P21 to P22. (Θ12−θ11) and (θ22−θ21) are approximately 360 degrees in any configuration.

  FIG. 7 is a graph showing the pressure change and the timing at which the circumferential groove 103 opens in the case of the asymmetric scroll in the conventional configuration shown in FIG. The pressure in the second compression chamber is smaller than that in the case of the symmetric scroll, but is still smaller in the first compression chamber. However, in the configuration of the present embodiment in FIG. 6, the pressures of both the compression chambers 11 a and 11 b can be made substantially equal, and high efficiency and high efficiency can be achieved by equalizing the amount of oil supply as in the case of the symmetrical scroll. Reliability can be realized.

  In addition, when liquid compression or oil compression occurs during transient operation or abnormal operation, the pressure in the second compression chamber 11b tends to rise abnormally, and backflow from the second compression chamber 11b to the oil supply hole 28 occurs. However, as shown in FIG. 2, it is easy to impair the reliability due to insufficient lubrication, but by making the distance from the lubrication hole 28 to the first lubrication passage outlet 30a smaller than the distance to the second lubrication passage outlet 30b, that is, By making the length of the second oil supply passage longer than the length of the first oil supply passage, the risk of backflow from the second compression chamber 11b to the oil supply hole 28 is reduced, and high reliability can be maintained. .

  In the present embodiment, the oil supply holes 28 and the respective oil supply passages are provided in the upper surface 9d of the orbiting scroll wrap to supply oil to the compression chambers 11a and 11b. The effect is obtained. At the same time, when the orbiting scroll 9 is operated by being pressed against the fixed scroll 6, it slides on the upper surface 6e of the fixed scroll lap, but since it can be directly supplied with oil, the sliding loss is improved by improving the lubricity of the sliding surface. It is also possible to realize reduction of wear, suppression of wear and seizure.

  In the present embodiment, the amount of oil supplied to the compression chambers 11a and 11b is equalized by setting the opening start volume ratio of the first oil supply passage outlet 30a to be equal to or greater than the opening start volume ratio of the second oil supply passage outlet 30b. Although high efficiency and high reliability are realized, the actual pressure is often different from the theoretical pressure due to leakage between both the compression chambers 11a and 11b, and conversely, the opening of the second oil supply passage outlet 30b starts. Even if the volume ratio is slightly increased, the amount of oil supply can be equalized.

  In the example of FIG. 2, both the oil supply passage outlets 30 a and 30 b are formed by arcs having a diameter larger than the width of the upper surface groove 29. With this configuration, the lubrication passage outlets 30a and 30b can be machined simultaneously with the same tool at the time of finishing the orbiting scroll wrap 9a, so that the depth can be managed with high accuracy and the variation in the lubrication amount can be suppressed. Is possible.

(Embodiment 2)
FIG. 8 is a front view of the orbiting scroll 9 according to the second embodiment of the present invention, in other words, another example of the orbiting scroll 9 shown in FIG. In FIG. 8, the orbiting scroll wrap 9a is provided with an oil supply hole 28 along the height direction, and an upper surface groove 29 including an opening of the oil supply hole 28 is formed on the upper surface 9d of the orbiting scroll wrap 9a. It is provided in the extending direction. Two outlets, a first oil supply passage outlet 30a that communicates with the first compression chamber 11a and a second oil supply passage outlet 30b that communicates with the second compression chamber 11b, are provided at both ends of the upper surface groove 29, and the width thereof is the upper surface groove. Equal to 29 width. In the example of FIG. 8, the outlet 30a and the outlet 30b are provided at different extension angles on the upper surface 9d.

  With this configuration, the upper surface groove 29 and the oil supply passage outlets 30a and 30b can be simultaneously processed with the same tool, so that the processing tact time can be shortened and the cost can be reduced.

(Embodiment 3)
9 and 10 are front views of still another example of the orbiting scroll 9 according to the third embodiment of the present invention, in other words, the orbiting scroll 9 shown in FIG. 9 and 10, the orbiting scroll wrap 9a is provided with an oil supply hole 28 in the height direction, and the upper surface 9d of the orbiting scroll wrap 9a includes an arcuate and linear upper surface groove 29 including the opening of the oil supply hole 28. Is provided so as to communicate with the first compression chamber 11a and the second compression chamber 11b. 9 and 10, the outlet 30a and the outlet 30b are provided at different extension angles on the upper surface 9d.

  With this configuration, since it is not necessary to process the upper surface groove 29 into a complicated shape, the processing tact time can be further shortened and the cost can be reduced.

  As described above, the scroll compressor according to the present invention can achieve high efficiency by reducing leakage loss, sliding loss, and viscous loss, and high reliability by preventing wear and seizure, and is an HFC (Hydro Fluoro). In addition to air conditioners and heat pump water heaters that use Carbon refrigerants and HCFC (Hydro Chloro Fluoro Carbon) refrigerants, they can also be used in applications such as air conditioners and heat pump water heaters using natural refrigerant carbon dioxide. .

The longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention Front view of an example of the orbiting scroll 9 shown in FIG. FIG. 2 is a view of the orbiting scroll 9 viewed from the back 9c side by combining the orbiting scroll 9 shown in FIG. 2 and the fixed scroll 6 shown in FIG. Graph of pressure change from closing of both compression chambers 11a and 11b to discharge in the case of a symmetrical scroll in which the closed volumes of the first compression chamber 11a and the second compression chamber 11b are equal. The graph which shows the pressure change in the case of symmetrical scroll in the conventional structure shown in FIG. 11, and the timing which the circumferential groove | channel 103 opens. Graph of pressure change from closing of both compression chambers 11a, 11b to discharge in the case of asymmetric scroll in which the confining volume of the first compression chamber 11a is larger than the confining volume of the second compression chamber 11b The graph which shows the timing of the pressure change and circumferential groove 103 opening in the case of asymmetric scroll in the conventional configuration shown in FIG. Front view of orbiting scroll 9 according to Embodiment 2 of the present invention Front view of orbiting scroll 9 according to Embodiment 3 of the present invention Front view of another orbiting scroll 9 according to Embodiment 3 of the present invention Front view of orbiting scroll in scroll compressor of Patent Document 1 The front view which shows the combination of the scroll wrap in the scroll compressor of patent document 2

6 fixed scroll 6b fixed scroll wrap 9 orbiting scroll 9a orbiting scroll wrap 11 compression chamber 28 oil supply port 29 upper surface groove 30a first oil supply passage outlet 30b second oil supply passage outlet

Claims (6)

The spiral fixed scroll wrap and the orbiting scroll wrap are meshed with each other to form at least a first compression chamber and a second compression chamber between the two scrolls. Each of the first compression chamber and the second compression chamber on the inner wall side of the orbiting scroll wrap is a scroll compressor whose volume changes, and an oil supply hole is formed on the upper surface of at least one of the orbiting scroll wrap and the fixed scroll wrap. A first oil supply passage that connects the opening of the oil supply hole and the first compression chamber, and a second oil supply passage that connects the opening of the oil supply hole and the second compression chamber are formed as the oil supply hole. Formed on the upper surface of the lap, and the outlets of the first oil supply passage and the second oil supply passage are different from each other on the lap in which the oil supply hole is formed. Provided at a position of the involute angle, the volume ratio of the first compression chamber when said first oil supply passage starts to open to the first compression chamber, the second oil supply passage is opened to the second compression chamber A scroll compressor characterized by being equal to or greater than a volume ratio of the second compression chamber when starting. Said closed narrowing the volume of the first compression chamber is greater asymmetric scroll than the volume confinement of the second compression chamber, the scroll compressor according to claim 1, wherein. The scroll compressor according to any one of claims 1 and 2 , wherein a length of the second oil supply passage is longer than a length of the first oil supply passage. The scroll compressor according to any one of claims 1 to 3 , wherein the oil supply hole and the oil supply passage are provided in an orbiting scroll wrap. The scroll compression according to any one of claims 1 to 3 , wherein the orbiting scroll is pressed against the fixed scroll to perform a compression operation, and the oil supply hole and the oil supply passage are provided in the fixed scroll wrap. Machine. The scroll compressor according to any one of claims 1 to 5 , wherein carbon dioxide is used as a working fluid.