CROSS-REFERENCE TO RELATED APPLICATIONS
This application claims the foreign priority benefit under 35 U.S.C. §119 of Japanese Patent Application No. 2011-110004, filed on May 17, the disclosure of which is incorporated herein by reference.
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to a sealed scroll compressor for use in refrigeration or air conditioning, and in particular to a sealed scroll compressor for helium.
2. Description of the Related Art
An example of a sealed scroll compressor for helium is disclosed in Japanese Patent Laid-open No. 2009-156234 (hereinafter referred to as JP2009-156234A).
The sealed scroll compressor disclosed in JP2009-156234A has an oil-injection mechanism, in which an oil-injection pipe for cooling the working helium gas is arranged through the wall of a sealed container and is connected to an oil-injection port arranged in an end plate of the stationary scroll. However, the flow rate of the first injected cooling oil into the outer compression chamber on the outer side of the scroll and the flow rate of the second injected cooling oil into the inner compression chamber on the inner side of the scroll are unbalanced, where the outer compression chamber is formed between the outer curved surface of the orbiting scroll (orbital scroll) and the inner curved surface of the stationary scroll, and the inner compression chamber is formed between the inner curved surface of the orbiting scroll and the outer curved surface of the stationary scroll. In other words, the injected cooling oil is not equally distributed to the inner compression chamber and the outer compression chamber in the conventional scroll compressor. FIG. 12 is a graph indicating the relationship between the pressures in the outer compression chamber and the inner compression chamber in a conventional sealed scroll compressor and the sealed scroll compressor according to an embodiment of the present invention (explained later) and the orbital angle of the orbiting scroll. As indicated in the curves indicating variations of the pressures P13 and P14 in the pressure chambers in the conventional sealed scroll compressor in FIG. 12, when the flow rate of the injected cooling oil into the inner compression chamber and the flow rate of the injected cooling oil into the outer compression chamber become unbalanced, the performance in isolating the compression chambers from each other is lowered. Therefore, the rate of the pressure increase (indicated by a compression curve) differs between the compression chambers, and the pressure difference (ΔPI) between the compression chambers increases. The increase in the pressure difference (ΔPI) between the compression chambers can increase the internal leakage. When the internal leakage is increased by the increased pressure difference between the compression chambers, the internal compression power increases, so that the compressor input increases. In addition, since the volume efficiency is lowered during the intake process, the flow rate of helium gas is lowered. Therefore, the performance of the compressor is lowered.
In view of the above, the object of the present invention is to improve the performance of the sealed scroll compressor.
SUMMARY OF THE INVENTION
In order to achieve the above object, according to the first aspect of the present invention, a sealed scroll compressor for helium is provided. The sealed scroll compressor includes: a sealed container; a stationary scroll being contained in the sealed container and having an end plate and a scroll wrap; an oil-injection port having an opening and being arranged in the end plate of the stationary scroll; an oil-injection mechanism having an oil-injection pipe which is arranged to pass through the sealed container and connected to the oil-injection port; and an orbiting scroll contained in the sealed container and interleaved with the stationary scroll to form an outer compression chamber and an inner compression chamber which realize an asymmetric-wrap type compression chambers. The opening of the oil-injection port is arranged at a bottom surface of a groove between ridges formed with the scroll wrap of the stationary scroll in such a manner that a first range of an orbital angle of the orbiting scroll is approximately identical to a second range of the orbital angle of the orbiting scroll, where the oil-injection port is connected to the outer compression chamber while the orbital angle of the orbiting scroll is in the first range, and is connected to the inner compression chamber while the orbital angle of the orbiting scroll is in the second range.
In addition, in order to achieve the aforementioned object, according to the second aspect of the present invention, a sealed scroll compressor for helium is provided. The sealed scroll compressor includes: a sealed container; a stationary scroll being contained in the sealed container and having an end plate and a scroll wrap; an oil-injection port having an opening and being arranged in the end plate of the stationary scroll; an oil-injection mechanism having an oil-injection pipe which is arranged to pass through the sealed container and connected to the oil-injection port; and an orbiting scroll contained in the sealed container and interleaved with the stationary scroll to form an outer compression chamber and an inner compression chamber which realize an asymmetric-wrap type compression chambers. The opening of the oil-injection port is arranged at a bottom surface of a groove between ridges formed with the wrap of the stationary scroll in such a manner that a first range θ1 of an orbital angle of the orbiting scroll, a second range θ2 of the orbital angle of the orbiting scroll, a first stroke volume Vth1 in the outer compression chamber, and a second stroke volume Vth2 in the inner compression chamber satisfy a relationship,
θ1/θ2≈Vth1/Vth2.
According to the present invention, the performance of the compressor is improved.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a vertical cross-sectional view of the entire structure of a vertical type sealed scroll compressor for helium according to the embodiment of the present invention;
FIG. 2 is a partial cross-sectional view illustrating part of the sealed scroll compressor of FIG. 1 realizing an oil-injection mechanism;
FIG. 3 is a plane view of a stationary scroll;
FIG. 4 is a vertical cross-sectional view of the stationary scroll;
FIG. 5 is a schematic plane view of an orbiting scroll;
FIG. 6 is a cross sectional view of a configuration in which the stationary and orbiting scroll wraps are assembled together, where the orbiting scroll is at the orbital angle θs1;
FIG. 7 is a cross sectional view of a configuration in which the stationary and orbiting scroll wraps are assembled together, where the orbiting scroll is at the orbital angle θs2;
FIG. 8 is a graph of compression curves in the pressure chambers (i.e., curves indicating variations of the pressures in the pressure chambers with the orbital angle of the orbiting scroll);
FIG. 9 is a partial plane view of a first variation of the stationary scroll, in which the oil-injection port is changed from the stationary scroll 5 of FIG. 3;
FIG. 10 is a graph of compression curves in the pressure chambers (i.e., curves indicating variations of the pressures in the pressure chambers with the orbital angle of the orbiting scroll) in a second variation of the embodiment, in which the oil-injection port is changed from the present embodiment;
FIG. 11 is a plane view of the second variation of the stationary scroll, in which the oil-injection port is displaced from the stationary scroll 5 of FIG. 8; and
FIG. 12 is a graph of compression curves in the pressure chambers (i.e., curves indicating variations of the pressures in the pressure chambers with the orbital angle of the orbiting scroll) in a conventional compressor and a compressor according to the embodiment.
DETAILED DESCRIPTION OF THE INVENTION
Hereinbelow, the embodiment of the present invention and variations are explained with reference to FIGS. 1 to 12.
First, the structure of the sealed scroll compressor according to the embodiment of the present invention and the flow of working helium gas and the flow of injected cooling oil are explained below with reference to FIGS. 1 and 2. FIG. 1 is a vertical cross-sectional view of the entire structure of the vertical type sealed scroll compressor for helium according to the present embodiment, and FIG. 2 is a partial cross-sectional view illustrating part of the sealed scroll compressor of FIG. 1 realizing an oil-injection mechanism. As illustrated in FIGS. 1 and 2, an oil-injection pipe 31 for injecting (cooling) oil (for use in cooling helium gas) passes through an upper cover 2a of a sealed container 1 and is connected to an oil-injection port 22, which is arranged in an end plate 5a of a stationary scroll 5. The opening of the oil-injection port 22 is arranged toward the edge face of a wrap 6b of an orbiting scroll 6. An intake pipe 17 is arranged on the upper side of the sealed container 1, and a scroll compressor mechanism and a motor unit 3 are respectively held in upper and lower parts in the sealed container 1. The inside of the sealed container 1 is separated by a frame 7 into a discharge chamber 1a and a motor chamber 1b.
Compression chambers 8a and 8b (which may be collectively referred to as the compression chambers 8) are formed in the scroll compressor mechanism by interleaving the stationary scroll 5 and the orbiting scroll 6 as illustrated in FIGS. 6 and 7. The stationary scroll 5 is constituted by the end plate 5a and a wrap 5b, where the end plate 5a has a round platelike shape, and the wrap 5b is arranged perpendicular to the end plate 5a and formed to have the shape of an involute (or a curve near to an involute) in every cross section parallel to the end plate 5a. In addition, a discharge port 10 is arranged in the center of the stationary scroll 5, and an intake port 15 is arranged in a peripheral part of the stationary scroll 5. The orbiting scroll 6 is constituted by an end plate 6a, the wrap 6b, and a boss 6c. The end plate 6a has a round platelike shape. The wrap 6b is arranged perpendicular to the end plate 6a and formed to have a shape similar to the wrap 5b of the stationary scroll 5. The boss 6c is formed on the side, opposite to the wrap 6b, of the end plate 6a. A main bearing 40 is formed in the center of the frame 7, and a rotating shaft 14 is supported by the main bearing 40. An eccentric shaft 14a, which is formed at the tip of the rotating shaft 14, is pivotally inserted into the boss 6c. The stationary scroll 5 is fixed to the frame 7 with multiple bolts. In addition, the orbiting scroll 6 is supported by the frame 7 through an Oldham mechanism 38 (which is constituted by an Oldham ring and Oldham keys) in such a manner that the orbiting scroll 6 orbits with respect to the stationary scroll 5 without being rotated.
A motor shaft 14b is integrally coupled to the rotating shaft 14, and is directly connected to the motor unit 3. The intake pipe 17 passes through the upper cover 2a of the sealed container 1, and is connected to the intake port 15 of the stationary scroll 5.
The discharge chamber 1a has the discharge port 10 as an opening, so that the discharge chamber 1a is connected to the motor chamber 1b through first paths 18a and 18b, which are arranged in peripheral regions of the frame 7. The motor chamber 1b is connected to a discharge pipe 20, which passes through a casing 2b. The casing 2b constitutes the central part of the sealed container 1. The discharge pipe 20 is located on the side of the sealed container 1 nearly opposite to the first paths 18a and 18b. The motor chamber 1b is separated by a (motor) stator 3a into an upper space 1b1 and a lower space 1b2. In addition, in order to allow the oil and gas to flow between the upper space 1b1 and the lower space 1b2, the upper space 1b1 and the lower space 1b2 are connected through paths 25b and 25c (which may be collectively referred to as the paths 25). The paths 25b and 25c are formed in the gaps between the motor stator 3a and the inner wall surface 2m of the casing 2b.
Further, the upper space 1b1 and the lower space 1b2 are also connected through the motor air gap 26. Since a mixture of the gas and the cooling oil flows in the motor chamber 1b through the above paths, the motor can be directly cooled with the injected oil, the temperature of which is relatively low (e.g., 60° C. to 70° C.).
An O-ring 53 is arranged between the intake pipe 17 and the stationary scroll 5 for hermetically separating the high-pressure region and the low-pressure region. In addition, a back-pressure chamber 36 is realized by the space located on the rear side of the end plate of the orbiting scroll 6. That is, the back-pressure chamber 36 is a space enclosed by the scroll compressor mechanism and the frame 7. An intermediate pressure between the intake pressure Ps and the discharge pressure Pd is introduced into the back-pressure chamber 36 through a pore 6d perforated through the end plate of the orbiting scroll 6, so that the intermediate pressure exerts force in the axial direction to the orbiting scroll 6, and presses the orbiting scroll 6 to the stationary scroll 5.
Lubricating oil 23 is reserved at the bottom of the sealed container 1. The lubricating oil 23 is sucked into an oil-suction tube 27 by the centrifugal pump effect which is produced by an eccentric cavity 13 arranged in the rotating shaft 14, flows in the rotating shaft 14, and is then supplied to a scroll bearing 32. The oil supplied to the scroll bearing 32 and discharged from the scroll bearing 32 drops to the main bearing 40 (which is a roller bearing), moves to the bottom end of the frame, is lead through a discharge tube 74, and returns to an oil reservoir in a bottom chamber 2c. In addition, the oil supplied to the scroll bearing 32 and discharged from the scroll bearing 32 moves to the back-pressure chamber 36 through a sealing means 85 which has a ring-shaped sealing structure.
As illustrated in FIG. 2, pocket pores 58 are arranged on the end face (facing the sealing means 85) of the boss 6c of the orbiting scroll 6, so that the oil in the pocket pores 58 is intermittently discharged to the back-pressure chamber 36 by the orbiting motion of the orbiting scroll 6. Then, the oil moved to the back-pressure chamber 36 is injected through the aforementioned pore 6d into only the outer compression chamber 8a (which is fanned on the outer side of the wrap 6b of the orbiting scroll 6), is mixed with compressed gas in the outer compression chamber 8a, and is thereafter discharged to the discharge chamber 1a together with the helium gas.
In order to drain the lubricating oil 23 accumulated at the bottom of the sealed container 1, an injected-oil outlet part 29 is arranged through the bottom of the sealed container 1, and an oil-drain pipe 30 is connected to the injected-oil outlet part 29. The lubricating oil 23 accumulated at the bottom of the sealed container 1 flows into the inflow part 30a of the outlet part 29 and flows through the oil-drain pipe 30 due to the difference between the discharge pressure Pd in the sealed container 1 and the internal pressures Pi1 and Pi2 (which may be collectively referred to as Pi) of the compression chambers 8. Further, a bore reduction means 30m is arranged in the path 30f inside the injected-oil outlet part 29, where the bore reduction means 30m has a diameter equivalent to the diameter of a bore reduction means 31m which is arranged in oil-injection piping.
Although the arrangement around the oil-injection pipe 31 are explained in detail later, the bore reduction means 31m is arranged in a path 31f which is located inside the oil-injection pipe 31 immediately in front of the oil-injection port 22 of the oil-injection pipe 31, where the diameter of the bore reduction means 31m is smaller than the diameter d0 of the oil-injection port 22.
FIG. 3 is a plane view of the stationary scroll 5, FIG. 4 is a vertical cross-sectional view of the stationary scroll 5, and FIG. 5 is a schematic plane view of the orbiting scroll 6. As illustrated in FIGS. 3 to 5 and as mentioned before, the stationary scroll 5 is constituted by the end plate 5a and a wrap 5b, where the end plate 5a has a round platelike shape, and the wrap 5b is arranged perpendicular to the end plate 5a and formed to have the shape of an involute (or a curve near to an involute) in every cross section parallel to the end plate 5a. In addition, a discharge port 10 is arranged in the center of the stationary scroll 5, and an intake port 15 (constituted by a first part 15a connected to the intake pipe 17 and a second part 15b connected to the first part 15a) is arranged in a peripheral part of the stationary scroll 5.
In the plane view illustrated in FIG. 3, Ok denotes the center of the coordinates, and Xk and Xk are coordinate axes. The point 64 is the outermost point of contact corresponding to the position at which the end of the wrap 6b comes in contact with the inner surface 561 of the stationary scroll 5 when the outer compression chamber 8a is formed (as illustrated in FIG. 6), and the point 63 is the outermost point of contact corresponding to the position at which the end of the wrap 6b comes in contact with the outer surface 562 of the stationary scroll 5 when the inner compression chamber 8b is formed (as illustrated in FIG. 7). That is, the outer compression chamber 8a is formed between the outer surface 661 of the orbiting scroll 6 and the inner surface 561 of the stationary scroll 5, and the inner compression chamber 8b is formed between the inner surface 662 of the orbiting scroll 6 and the outer surface 562 of the stationary scroll 5. In the plane view of FIG. 3, the point 64 (indicating the outermost position of contact with the end of the wrap 6b when the outer compression chamber 8a is formed) is the end of a scroll wrap curve which is extended from the end point 63 of the scroll wrap curve of the outer surface 562 of the stationary scroll 5 by at most π rad, where it is the circle ratio (i.e., the ratio of the circumference to the diameter of a circle). The above scroll wrap curve realizes asymmetric-wrap type compression chambers. For example, in the arrangement illustrated in FIG. 7, the meaning of the “asymmetric-wrap type” is that the pressures in the outer and inner compression chambers 8a and 8b (which have crescent-like cross sections) are different, i.e., the compression chambers 8a and 8b are asymmetric with respect to the pressure, although the volumes of the compression chambers 8a and 8b (and the cross sections of the compression chambers 8a and 8b) are identical. Such a scroll compressor is called a asymmetric-wrap type compressor. The angle at which the scroll wrap ends may be indicated by the involute scroll angle.
In order to cool the body of the compressor and lower the temperature of the helium gas which is heated by adiabatic compression, the sealed scroll compressor according to the present invention has the structure for injection of oil for cooling. In the structure, the oil-injection port 22 is a single port, and is slightly displaced outward, in the plane view parallel to the end plate 5a, from the center of a groove between ridges formed with the wrap 5b as illustrated in FIGS. 3 and 4. The opening diameter d0 of the oil-injection port 22 is set to satisfy d0>t, where t is the thickness of the scroll wrap 6b. Thus, it is possible to avoid covering of the oil-injection port 22 by the thickness of the teeth (i.e., the edge of the scroll wrap 6b).
As illustrated in FIG. 4, a round bore 22a for insertion of the path 31m is arranged immediately in front of the oil-injection port 22 in the stationary scroll 5. The oil-injection port 22 is arranged to have an opening at the bottom surface 5m of the groove between the ridges formed with the wrap 5b, and the center 22f of the opening of the oil-injection port 22 is located at a position displaced from the end 63 or 64 of the scroll wrap 6b toward the inner end (at the origin Ok) of the wrap 5b along the scroll of the wrap 5b by the scroll wrap angle Δλ0 of approximately 1.5 π rad, where it is the circle ratio. The stroke volume Vth1 of the outer compression chamber 8a and the stroke volume Vth2 of the inner compression chamber 8b satisfy the relationship Vth1>Vth2, and the ratio Vth1/Vth2 is approximately 1.1 to 1.2. Therefore, control of the flow rates of the cooling oil injected into the outer and inner compression chambers 8a and 8b according to the flow rates Vth1 and Vth2 of intake gas is effective in cooling.
In order to achieve the above effect, the center 22f of the oil-injection port 22 is slightly displaced outward (i.e., toward the inner surface 561 of the stationary scroll 5) from the center of the groove between the ridges formed with the wrap 5b, as illustrated in the plane view of FIG. 3 or the vertical cross-sectional view of FIG. 4. Specifically, the ratio S2/Dt of the distance S2 between the inner surface 561 of the stationary scroll 5 and the center 22f of the oil-injection port 22 to the width Dt of the groove between the ridges formed with the wrap 5b is approximately 0.45 to 0.48 in this example.
In the plane view of FIG. 5, the wrap 6h in the orbiting scroll 6 is formed to realize the outer surface 661 of which ends with an outer end portion 6k. The points 82a and 83a are at the scroll wrap angle at which the scroll wrap 6b ends. As illustrated in the plane view of FIG. 5, the points 82a and 83a in the outer end portion 6k of the wrap 6b are smoothly connected through an arc having a radius R4 in every cross section parallel to the end plate 6a. That is the outer surface 661 of the orbiting scroll 6 and the inner surface 662 of the orbiting scroll 6 are continuously connected at the outer end portion 6k with the arc radius R4. Similarly, the outer surface 661 of the orbiting scroll 6 and the inner surface 662 of the orbiting scroll 6 are continuously connected at an inner end portion 6n with an arc radius R5. In addition, the aforementioned single pore 6d, which passes through the end plate 6a, is singly arranged at a position along the outer surface 661 of the orbiting scroll 6.
FIG. 6 is a cross sectional view of a state, at completion of a process of intake into the outer compression chamber 8a, of a configuration in which the stationary scroll 5 and the orbiting scroll 6 are assembled. In the state of FIG. 6, the orbiting scroll 6 is at the angular position of the orbital angle θs1, at which the opening of the oil-injection port 22 is connected to only the outer compression chamber 8a.
FIG. 7 is a cross sectional view of a state, at completion of a process of intake into the inner compression chamber 8b, of the configuration in which the stationary scroll 5 and the orbiting scroll 6 are assembled. In the state of FIG. 7, the orbiting scroll 6 is at the angular position of the orbital angle θs2, at which the opening of the oil-injection port 22 is connected to only the inner compression chamber 8b.
FIG. 8 is a graph of compression curves in the pressure chambers (i.e., curves indicating variations of the pressures in the pressure chambers with the orbital angle of the orbiting scroll 6). FIG. 8 indicates variations in the pressure Pi1 in the outer compression chamber 8a and the pressure Pi2 in the inner compression chamber 8b while the orbital angle varies π rad. The angular position of the orbital angle θs1 is the position at which compression of the outer compression chamber 8a starts, and the angular position of the orbital angle θs2 is the position at which compression of the inner compression chamber 8b starts.
As mentioned before, the opening of the oil-injection port 22 is arranged at the bottom surface 5m of the groove between the ridges formed with the wrap 5b in the stationary scroll 5. In this case, the range (width) θ1 of the orbital angle in which the outer compression chamber 8a is connected to the oil-injection port 22 and the range (width) θ2 of the orbital angle in which the inner compression chamber 8b is connected to the oil-injection port 22 can be set to make the ratio θ1/θ2 as great as (nearly equal to) the ratio V0=Vth1/Vth2. In the example of FIG. 3, the ratio θ1/θ2 is approximately 1.1 to 1.2.
FIG. 8 indicates that the operation of injecting the oil is started at the angle which is θ5 before the orbital angle θs1, where the process of intake into the outer compression chamber 8a is completed at the orbital angle θs1. In this case, the intake chamber 5f formed outside the wrap 5b is connected to the oil-injection port 22 while the orbital angle of the orbiting scroll 6 is in the range θ5. That is, the intake chamber 5f formed outside the wrap 5b is intermittently connected to the oil-injection port 22, so that the helium gas in the intake chamber 5f is cooled. In addition, while the orbital angle of the orbiting scroll 6 is in the range θ6, both of the outer and inner compression chambers 8a and 8b are concurrently connected to the oil-injection port 22 (or to the port 228 in the first variation illustrated in FIG. 9). The range θ5, in which the intake chamber 5f is connected to the oil-injection port 22, is adjusted by arranging the opening of the oil-injection port 22 at the groove bottom between the ridges of the wrap 5b in such a manner that the center of the opening of the oil-injection port 22 is displaced outward from the center of the width of the groove bottom.
FIG. 9 is a plane view of a first variation of the stationary scroll in the sealed scroll compressor according to the embodiment. The first variation of the embodiment is different from the stationary scroll 5 illustrated in FIG. 3 in the shape of the opening 228 of the oil-injection port, and the opening 228 of the oil-injection port is elongated in the radial direction. Practically, the dimension L7 of the opening 228 in the radial direction is approximately 2.5 times the thickness t of the wrap 5b, and the dimension L8 of the opening 228 in the circumferential direction is set at most equivalent to the thickness t of the wrap 5b. The range (width) θ1 of the orbital angle in which the outer compression chamber 8a is connected to the oil-injection port 228 can be set by adjusting the dimension L7 of the opening 228 in the radial direction. Further, both of the outer and inner compression chambers 8a and 8b can be concurrently connected to the oil-injection port 22 in the case where the opening diameter d0 of the oil-injection port 22 is set to satisfy d0>t, and both of the outer and inner compression chambers 8a and 8b can be concurrently connected to the oil-injection port 228 in the case where the dimension L7 of the opening 228 in the radial direction is set to satisfy L7>t.
Since the means for equally distributing the injected oil according to the present embodiment can relatively reduce the variations in the pressure difference in oil injection (i.e., the differences between the discharge pressure Pd and the pressures Pi1 and Pi2 in the outer and inner compression chambers 8a and 8b) and reduce the oil hammer effect which is caused when the oil is injected. Therefore, it is possible to reduce vibration in the oil injection piping and the piping stress. Further, it is possible to suppress the flow sound (pulsating sound) inside the oil-injection piping, and therefore reduce the noise and vibration of the compressor.
FIG. 11 is a plane view of a second variation of the stationary scroll in the sealed scroll compressor according to the present embodiment. As illustrated in FIG. 11, the second variation of the embodiment is different from the first variation in that the opening 222 of the oil-injection port in the second variation (illustrated in FIG. 11) is located at a position displaced from the position of the opening 228 of the oil-injection port in the first variation (illustrated in FIG. 9) toward the inner end (at the origin Ok) of the wrap 5b along the scroll of the wrap 5b by the scroll wrap angle of approximately 0.5 π rad, where π is the circle ratio. Similarly to the first variation, the opening 222 of the oil-injection port is elongated in the radial direction.
FIG. 10 is a graph of compression curves in the outer and inner compression chambers 8a and 8b (i.e., curves indicating variations of the pressures in the outer and inner compression chambers 8a and 8b with the orbital angle of the orbiting scroll 6) in the second variation. In FIG. 10, the range (width) θ3 of the orbital angle in which the outer compression chamber 8a is connected to the oil-injection port 222 and the range (width) θ4 of the orbital angle in which the inner compression chamber 8b is connected to the oil-injection port 222 are almost equalized (i.e., θ3≈θ4). Practically, each of the ranges θ3 and θ4 has a width of approximately 200 to 230 degrees. In addition, while the orbital angle of the orbiting scroll 6 is in the range θ7, both of the outer and inner compression chambers 8a and 8b are concurrently connected to the oil-injection port 222.
The sealed scroll compressors according to the present embodiment and the first and second variations are characterized in that the center of the opening of the oil-injection port 22, 228, or 222 is located at a position displaced from the end 63 or 64 of the scroll wrap 5b toward the inner end (at the origin Ok) of the wrap 5b along the scroll of the wrap 5b by the scroll wrap angle Δλ0 of approximately 1.5 π to 2 π rad, where π is the circle ratio.
In the sealed scroll compressors according to the present embodiment and the first and second variations, the oil flowing into the oil-drain pipe 30 passes through external oil piping 51 and is then inputted into an oil cooler 33. After the oil is cooled in the oil cooler 33, the cooled oil passes through the oil-injection pipe 31 and the oil-injection port 22 (or 228 or 222) and is injected into the outer and inner compression chambers 8a and 8b. As illustrated in FIG. 2, an O-ring 48 is arranged around the bore reduction means 31 m for hermetically isolating the pressure in the oil-injection pipe 31 from the high pressure in the discharge chamber 1a.
The structures and mechanisms explained above enables equal distribution of the injected cooling oil into the outer and inner compression chambers, and achieves uniformity in the cooling performance. As indicated in the curves indicating variations of the pressures Pi1 and Pi2 in the pressure chambers in the embodiment and the curves indicating variations of the pressures Pi3 and Pi4 in the pressure chambers in the conventional sealed scroll compressor, the oil-injection function which equally distributes the injected oil to the outer and inner compression chambers 8a and 8b enhances the effect of the cooling oil in isolating the outer and inner compression chambers from each other, so that the rates of the pressure increase (indicated by the compression curves) in the present embodiment is lower than the conventional sealed scroll compressor. Therefore, for example, the pressure difference (ΔP2) between the adjacent compression chambers in the present embodiment is smaller than the pressure difference (ΔP1) between the adjacent compression chambers in the conventional sealed scroll compressor. The decrease in the pressure difference between the adjacent compression chambers reduces the internal leakage and the compression power, and increases the volume efficiency. Thus, the performance and the efficiency of the compressor are greatly improved. In addition, the cooling oil equally distributed to the outer and inner compression chambers 8a and 8b enhances the effects of cooling and isolating the working gas in the outer and inner compression chambers 8a and 8b, and achieves thorough and effective lubrication of the sliding parts such as the edges of the scroll wraps. Further, since the compression power is reduced, the loads acting on the sliding parts such as the bearings are also reduced, so that the reliability of the compressor increases. Furthermore, the decrease in the bearing loads increases the lifetimes of the antifriction bearings such as the main bearing 40 and the scroll bearing 64.
Patent Application
20120294748
