Rotating scroll compressor

Abstract: A rotating type scroll compressor according to the present invention having a closed shell (1) that houses an electric drive member (2) and a scroll compressing member (3), the scroll compressing member having a drive scroll member (14) and a follower scroll member (15), the drive scroll member having a spiral shape lap (17) formed on a end plate (16) and being driven by the electric drive member, the follower scroll member having a center axial line that deviates from a center axial line of the drive scroll member and a spiral shape lap (21) fitting to the lap of the drive scroll member, said rotating type scroll compressor comprising rotating shaft portions (53) to which radial force of the rotating drive scroll member and the follower scroll member is applied, said rotating shaft portions being disposed at an upper portion and a lower portion of the laps to which the radial load of fluid is applied.

Description: BACKGROUND OF THE INVENTION The present invention relates to a rotating type scroll compressor for use with a freezing, air-conditioning, and hot water supplying fluid apparatuses, in particular, to improvements of supporting a scroll member of a rotating type scroll compressor and sealing in radial direction thereof. As a first related art reference, FIG. 8A is a vertical sectional view of an embodiment of a scroll compressor as disclosed in Japanese Patent Laid-Open Publication No. 4-8888. FIG. 8B is a sectional view taken along line A - A of FIG. 8A. Next, the outline of the embodiment will be described. In FIGS. 8A and 8B, reference numeral 1 is a closed shell. An electric drive member 2 is housed at a lower position of the shell. A scroll compressing member 3 is housed at an upper portion of the shell. The electric drive member 2 is composed of a startor 4 and a rotor 5 disposed therein. Between the startor 4 and the rotor 5, an air gap 6 is formed. A passage 7 with a partial cut-out is formed on the outer periphery of the startor 4. Reference numeral 8 is a main frame in contact with the inner wall of the closed shell 1. A main bearing 9 is disposed at the center of the main frame. Reference numeral 10 is an auxiliary frame in contact with the inner wall of the closed shell 1. The auxiliary frame has a sliding groove 11 that has an oval hole. The main frame 8 and the auxiliary frame 10 are secured by bolts 13 so as to form a cavity chamber 12. The scroll compressing member 3 is composed of a first scroll 14 and a second scroll 15. The first scroll 14 is driven by the electric drive member 2. The second scroll 15 rotates in the same direction as the first scroll 14. The first scroll 14 is composed of a cylindrical end plate 16, a spiral lap 17, and a main drive shaft 18. The spiral lap 17 is shaped in an involute curve. The main drive shaft 18 protrudes to the center of the other surface of the end plate 16. The first scroll 14 composes a drive side scroll. The second scroll 15 is composed of a cylindrical end plate 19, a ring shape wall 20, a spiral shape lap 21, and a follower shaft 22. The ring shape wall 20 protrudes to one surface periphery of the end plate and slides on the end plate 16 of the first scroll 14. The spiral shape lap 21 is surrounded by the ring shape wall and formed on the end plate 19. The spiral shape lap 21 is shaped in a tooth shape with a compensated involute angle. The follower shaft 22 protrudes to the center of the other surface of the end plate 19. The second scroll 15 composes a follower scroll. The laps 17 and 21 fit each other in the cavity chamber 12 so that the first and second scrolls 14 and 15 form a plurality of compression spaces 23. The main frame 8 and the auxiliary frame 10 partition the closed shell 1 as a low pressure chamber 24 and a high pressure chamber 24. Reference numeral 26 is a drive device. The drive device 26 is composed of a drive pin 27 and a guide groove 28. The drive pin 27 protrudes to the outer periphery of the end plate 16 of the first scroll 14. The guide groove 28 is formed in the radial direction of the ring shape wall 20 of the second scroll 15. The guide groove is shaped in an U letter shape with an outer cut-out. The circular path of the outer peripheral edge of the guide groove 28 is formed on the outer side of the circular path at the center of the drive pin 27. Reference numeral 29 is an eccentric bearing member slidably fits to the sliding groove 11. The eccentric bearing member is composed of an eccentric bush 31 and springs 32 and 33. The eccentric bush 31 has a hole 30 into which the follower shaft 22 of the second scroll 15 is rotatably inserted. The springs 32 and 33 hold the bush from both the sides. The main drive shaft 18 has a discharge hole 34 from which coolant compressed in the compression space 23 is discharged to a high pressure chamber 25. The discharge hole has two discharge openings 35 and 36 that open to the upper portion and the lower portion of the electric drive member 2. The follower shaft 22 has an intake hole 37 that guides the coolant in the low pressure chamber 24 to the compression space 23. Reference numeral 38 is a connection passage formed on the end plate 19. The passage 38 is connected to the air intake hole 37 so as to deliver the coolant to the compression space 23. Reference numeral 39 is a small hole formed on the end plate 16 of the first scroll 14. The small hole 39 is connected to the compression space 23 in which the coolant being compressed and the cavity chamber 12. The cavity chamber 12 and the low pressure chamber 24 are sealed by a seal member 40 formed on the sliding surface of the end plate 19 of the auxiliary frame 10 and the second scroll 15. The cavity chamber 12 and the high pressure chamber 25 are sealed by a seal member 41 formed on the sliding surface of the main bearing 9 and the main drive shaft 18. Reference numeral 42 is an intake pipe. The intake pipe 42 is connected to the low pressure chamber 24. Reference numeral 43 is a discharge pipe that is connected to the high pressure chamber 25. When the electric drive member 2 of the scroll compressor is rotated, the rotating force is transmitted to the first scroll 14 through the main drive shaft 18. The rotating force of the first scroll 14 is transmitted to the second scroll 15 through the drive device 26 so that the second scroll 15 rotates in the same direction as the first scroll 14. The center position of the eccentric bearing member 29 that fits to the sliding groove 11 deviates from the center of the main drive shaft 18 of the first scroll 14 so that the second scroll 15 rotates about the follower shaft 22. The first scroll 14 and the second scroll 15 gradually decrease the compression space 23 formed by these scrolls. The coolant that flows from the intake pipe 42 to the low pressure chamber 24 flows from the intake hole 37 of the follower shaft 22 to the compression space 23 through the passage 38 of the end plate 19 so as to compress the coolant. The compressed coolant is discharged from the discharge openings 35 and 36 to the high pressure chamber 25 through the discharge hole 34 formed on the main drive shaft 18 of the first scroll 14. The compressed coolant is discharged to the outside of the closed shell 1 from the discharge pipe 43. The coolant at the intermediate pressure that is being compressed is discharged from the small hole 39 to the cavity chamber 12 so that the resultant compressed coolant works as the back pressure of the first and second scrolls 14 and 15. With a predetermined clearance of the forward edges of the laps 17 and 21 of the scrolls, the end plates 16 and 19 are slid. Since the drive device 26 that rotates the second scroll 15 in the same direction as the first scroll 14 forms the circular path at the outer peripheral edge of the guide groove 28 at the outside of the circular path at the center of the drive pin 27, the drive pin 27 can be prevented from dropping from the guide groove 28. The drive pin 27 rotates the second scroll 15 in the same direction as the rotating direction of the first scroll 14 so that the compression space 23 is compressed. Since the center position of the follower shaft 22 is formed in a spiral shape that is an involute shape curve and the lap 21 of the second scroll 15 is formed in a spiral shape that is a tooth shape curve with a compensated involute angle, when both the first scroll 14 and the second scroll 15 are rotated in the same direction, the compression space 23 is compressed so as to prevent the contact portions of the laps 7 and 21 from being disengaged and them from abnormally contacted. Since the seal members 40 and 41 seal the low pressure chamber 24 and the high pressure chamber 25, the low pressure coolant and the high pressure coolant are prevented from entering the cavity chamber 12. The pressure in the cavity chamber 12 is kept at a predetermined intermediate pressure so that the axial sealing force of the first and second scrolls 14 and 15 are maintained in a proper level. Since the coolant compressed in the compression space 23 is discharged from the upper discharge opening 35 of the electric drive member 2 and the lower discharge opening 36 thereof to the high pressure chamber 25 through the discharge hole 34, the pressure drop of the coolant discharged to the high pressure chamber 25 can be suppressed and the coolant discharged from the discharging opening 36 flows to the discharge pipe 43 through the air gap 6 and the passage 7 of the electric drive member 2, thereby effectively cooling the electric drive member 2 and effectively using the heat given off from the electric drive member 2. Since the eccentric bearing member 29 is composed of the eccentric bush 31 (which causes the follower shaft 22 of the second scroll 15 to fit to the hole 30 in the sliding groove 11) and the springs 32 and 33 (which hold the eccentric bush 31 from both the sides). Thus, the center of the follower shaft 22 deviates from the center of the main drive shaft 18. In addition, since the springs 32 and 33 hold the eccentric bush 31, when an abnormally high pressure takes place in the compression space 23, the eccentric bush 31 is moved against the elastic force of the springs 32 and 33 in the sliding groove 11 of the oval hole so as to disengage the lap 21 of the second scroll 15 from the lap 17 of the first scroll 14. In addition, since the eccentric bearing member 29 does not rotate, the springs 32 and 33, which hold the eccentric bush 31, are not affected by centrifugal force, thereby preventing the spring constants from varying. By the above-described structure, when an abnormally high pressure takes place, the gap in the radial direction of the laps of the first scroll and the second scroll can be widened. As a second related art reference, an embodiment of a scroll compressor as disclosed in Japanese Patent Laid-Open Publication No. 4-12182 will be described. FIG. 9 is a vertical sectional view of this embodiment. For simplicity, the same portions as the first related art reference are denoted by the same reference numerals. Only the different points will be described. A follower shaft 22 of a second scroll 15 rotates only against an auxiliary frame 10a. The follower shaft 22 does not slide in the radial direction. A seal member 40a is formed between the follower shaft 22 and an auxiliary frame 10a. At discharge openings 35 and 36 formed on a main drive shaft 18, holders 44 and 45, springs 46 and 47, and check valves 50 and 51 are formed. The holders 44 and 45 are mounted on the main drive shaft 18. The check valves 50 and 51 are formed of heavy valves 48 and 49. By the above-descried structure, when the apparatus is operated, centrifugal force is applied to the check valves so as to always open the check valves. With the pressure difference between the discharge hole and the high pressure chamber, the check valves are prevented from being opened and closed. When the apparatus is stopped, it is prevented from being reversely rotated. As a third related art reference, a scroll type fluid discharging apparatus as disclosed in Japanese Patent Laid-Open Publication No. 50-32512 will be described. FIG. 10 is a horizontal sectional view of a scroll portion of the scroll type fluid discharging apparatus. The outline of the apparatus will be described. A compressor as discussed in connection with Fig. 10 is also known from WO-A-93/17241. Reference numerals 140 and 141 are two involute spiral laps of a fixed scroll member. Reference numerals 142 and 143 are two involute spiral laps of a moving scroll member. As a means for connecting the fixed scroll member and the moving scroll member, a ring 144 is disposed outside both the laps. Radial protrusions 155 and 156 of the fixed scroll member are slidably formed at a lower groove of the ring 144. Radial protrusions 157 and 158 secured to the laps 140 and 141 slidably fit to an upper groove of the ring 144. While the apparatus is being driven, the moving laps 142 and 143 are pressed to the fixing laps 140 and 141 by centrifugal force so as to hold a radial seal in the compression space. Each of the rotating type scroll compressors described as the first and second related art references has a shaft portion on the rear surface of the mirror surface on which the scroll lap is formed. The shaft portion is supported in an over-hang structure at a position apart from the lap to which the load of the compressed fluid is applied. Thus, the moment at which the scroll member becomes unstably may take place. In addition, the radial seal technique in the compression space of the scrolls uses centrifugal force in the case of the sliding type as described in the third related art reference. However, in the rotating type, since both the laps are rotated, the centrifugal force cannot be used. Thus, to improve the efficiency, the gap in the radial direction should be minimized. In the conventional fixed eccentric system, the assembling accuracy was very important. SUMMARY OF THE INVENTION According to the rotating scroll compressor of the present invention, rotating shaft portions that are affected by radial force of a rotating drive scroll portion and a follower scroll portion are disposed at upper and lower laps and support bearings are disposed at upper and lower portions of scroll laps. Thus, the unstable moment can be completely removed and thereby the scroll members can stably operated. In addition, since the shaft that supports one scroll is radially moved against the bearing that supports the other scroll, the shaft that supports the first scroll is radially moved corresponding to the load of the compressed fluid against the bearing that supports the second scroll. Thus, since the radial gap can be easily removed, the apparatus can be effectively operated without high assembling accuracy. These and other objects, features and advantages of the present invention will become more apparent in light of the following detailed description of a best mode embodiment thereof, as illustrated in the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is a vertical sectional view of a rotating type scroll compressor according to a first embodiment of the present invention; FIG. 2 shows a rotating type scroll compressor according to a second embodiment of the present invention, FIG. 2A is an enlarged vertical sectional view of a scroll portion, FIG. 2B is a sectional view taken along line X - X of FIG. 2A; FIG. 3 is a rotating type scroll compressor according to a third embodiment of the present invention; FIG. 3A is an enlarged vertical sectional view of a scroll portion, FIG. 3B is a sectional view taken along line Y - Y of FIG. 3A; FIG. 4 is a rotating type scroll compressor not according to the present invention; FIG. 4A is a vertical sectional view, FIG. 4B is a sectional view taken along line B - B of FIG. 4A, FIG. 4C is a schematic diagram for explaining the load applied to a scroll member; FIG. 5 shows a rotating type scroll compressor not according to the present invention, FIG. 5A is a vertical sectional view, FIG. 5B is a sectional view taken along line C - C of FIG. 5A; FIG. 6 shows a rotating type scroll compressor not according to the present invention, FIG. 6A is a vertical sectional view, FIG. 6B is a sectional view taken along line D - D of FIG. 6A; FIG. 7 shows a rotating type scroll compressor not according to the present invention, FIG. 7A is a vertical sectional view, FIG. 7B is a sectional view taken along line E - E of FIG. 7A; FIG. 8 shows a conventional scroll compressor, FIG. 8A is a vertical sectional view, FIG. 8B is a sectional view taken along line A - A of FIG. 8A; FIG. 9 is a vertical sectional view showing another conventional scroll compressor; and FIG. 10 is a horizontal sectional view showing a scroll portion of a conventional scroll type fluid discharging apparatus. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, with reference to FIGS. 1 to 3, embodiments of rotating type scroll compressors according to the present invention will be described. FIGS. 1 to 3 accord with the invention of claims 1 to 6. FIG. 1 is a vertical sectional view showing a rotating type scroll compressor according to a first embodiment of the present invention. For simplicity, in FIG. 1, the same portions as the structure shown in FIG. 8 are denoted by the same reference numerals. Only the different points will be described. A drive scroll member (first scroll) 14 has a scroll lap 17 and a rotating shaft portion (rotating shaft) 18. The scroll lap 17 is disposed on a end plate 16. The rotating shaft 18 is disposed on the opposite side of the scroll lap 17. A vertical member 16a extends on the scroll lap side of the outer peripheral portion of the end plate 16. A rotary annular plate 53 is secured to the vertical member 16a by a bolt 13b. The rotating center axial line of the bearing portion 54 of the rotary annular plate 53 accords with the rotating center axial line of the rotating shaft 18. The drive scroll member 14 is supported by a lower main bearing 9b and an upper bearing member 10b and rotated by the rotating shaft 18. The upper bearing member 10b supports the inner cylindrical bearing surface 54 of the upper bearing portion 53 of the drive scroll member 14 at an outer cylindrical bearing surface 10ba. In addition, the upper bearing member 10b and an inner cylindrical bearing surface 10bb support the outer cylindrical bearing surface 30 of the rotating shaft portion 22 of the follower scroll member (second scroll) 15. Reference numeral 31b is a bush. The center axial line of the outer cylindrical bearing surface 10ba of the upper bearing member 10b and the center axial line of the inner cylindrical bearing surface 10bb are eccentrically formed corresponding to the eccentric amount of the scroll members 14 and 15, respectively. The rotary annular plate 53 is an auxiliary bearing of the drive scroll member 14. The rotary annular plate 53 axially nips the scroll member 15 and functions as a restricting member against the axial motion. In addition, the rotary annular plate 53 prevents the freezing performance from lowering at the initial operation of the apparatus. A ring shape intermediate pressure chamber 55 is formed between the auxiliary bearing member 53 and the end plate 19. The intermediate chamber 55 has a sealing member 55b with an O ring. The intermediate chamber 55 is connected to the compression space 23 through a small hole 55a. Thus, a back-pressure is applied to the follower scroll member so as to reduce the load in the thrust direction. Since the radial load works for the laps, the structure with the bearings disposed at the upper and lower portions of the laps, the rotating operation can be much stably performed than the conventional over-hang structure. FIG. 2 shows a rotating scroll compressor according to a second embodiment of the present invention. FIG. 2A is an enlarged vertical sectional view showing a scroll portion. FIG. 2B is a sectional view taken along line X - X of FIG. 2A. The structure of the second embodiment is nearly the same as that shown in FIG. 1. For simplicity, the same portions as the structure of the first embodiment are denoted by the same reference numerals. Only the different points will be described. An upper bearing member 10c is divided into a portion 10'ca that contains an outer cylindrical bearing surface 10ca and a portion 10'cb that contains an inner cylindrical bearing surface 10cb. Both the portions are secured by bolts 56. As shown in FIG. 2B, since a center axial line B of the portion 10'ca, which contains the outer cylindrical bearing surface 10ca, deviates from a center axial line A of the portion 10'ca, which contains the inner cylindrical bearing surface 10cb. Thus, by rotating the portion 10'cb containing the inner cylindrical bearing surface 10cb and adjusting an eccentric amount E of a main drive shaft 18 against a center axial line A of a follower shaft 22, the bolts 56 (see FIG. 2A) are tightened so as to assemble them. FIG. 3 shows a rotating type scroll compressor according to a third embodiment of the present invention. FIG. 3A is an enlarged vertical sectional view of a scroll portion. FIG. 3B is a sectional view taken along line Y - Y of FIG. 3A. The structure of the third embodiment is nearly the same as that shown in FIG. 1. For simplicity, the same portions as the structure shown in FIG. 1 are denoted by the same reference numerals. Only the different points will be described. As with the second embodiment, an upper bearing portion 10d is divided into a portion 10'da that contains an outer peripheral portion 10da and a portion 10'db that contains an inner cylindrical bearing surface 10db. The portion 10'db, which contains the inner cylindrical bearing surface 10db, deviates from the portion 10'da, which contains the outer cylindrical bearing surface 10da. The portion 10'db is relatively moved against the portion 10'da for a predetermined length. While the apparatus is being operated, with the load of the radial fluid that works for the scroll member 15, a center axial line A of the inner cylindrical bearing surface 10db is set so that an eccentric amount E (see FIG. 3B) of the portion 10'da containing the outer cylindrical bearing surface 10da increases against the inner cylindrical bearing surface 10db due to the radial load of the fluid that works for the scroll member 15. Thus, while the apparatus is being operated, the fluid pressure causes the portion 10'da, which contains the outer cylindrical bearing surface 10da, and the portion 10'db, which contains the inner cylindrical bearing surface 10db to rotate in the direction of which the distance between A and B increases. Thus, the laps 17 and 21 in the radial direction can be completely sealed. According to the rotating type scroll compressors of the present invention, as described in the above-mentioned various embodiments, with a relatively simple changeof a structure, the operation of the scroll member becomes stable, thereby preventing the noise and reducing wear-out of the apparatus. In addition, the gap between the laps can be easily adjusted without high assembling accuracy. Thus, the machining steps and assembling steps can be reduced so as to reduce the cost of the apparatus. Moreover, the coefficient of compresibility (C.O.P) can be improved. Although the present invention has been shown and described with respect to a best mode embodiment thereof, it should be understood by those skilled in the art that the foregoing and various other changes, omissions, and additions in the form and detail thereof may be made therein without departing from the scope of the present invention.

Claims: A rotating type scroll compressor comprising a scroll compressing unit having: a drive scroll member (14) having a first spiral shape lap (17) formed on an end plate (16) and being driven by an electric drive unit (2), a follower scroll member (15) having a second spiral shape lap (21) fitting to said first lap (17) of the drive scroll member (14), a first rotating shaft portion (18) comprising a rotating shaft member affixed to said end plate (16) and disposed at a lower portion of the laps (17, 21), a second rotating shaft portion affixed to said end plate (16) and comprising an second rotating shaft portion or annular plate (53) disposed at an upper portion of the laps (17, 21), and an upper bearing member (10b, 10c, 10d) disposed at said upper portion of said laps (17, 21) and supporting a rotating follower shaft member (22) of the follower scroll member (15) at an inner cylindrical bearing surface (10bb, 10cb, 10db) thereof, wherein radial loads applied to said first and second laps (17, 21) are received through said first rotating shaft portion (18) by a main bearing (9b) disposed at a lower portion of said laps (17, 21) and supporting said rotating shaft member (18), characterized in that a bearing surface (54) is affixed to said annular plate (53), and said upper bearing member (10b, 10c, 10d) supports said bearing surface (54) at an outer cylindrical bearing surface (10ba, 10ca, 10da), so that the radial loads applied to said first and second laps (17, 21) are received through said second rotating shaft portion by said upper bearing member (10b, 10c, 10d), too, said upper bearing member (10b, 10c, 10d) including means for adjustably setting the eccentricity between said bearing surface (54) and the central axial line of the follower scroll member. The rotating type scroll compressor as set forth in claim 1, wherein said bearing member (10c, 10d) is divided into an outer bearing portion (10'ca, 10'da) which contains said outer cylindrical bearing surface (10ca, 10da) of said bearing member (10c, 10d), and into an inner bearing portion (10'cb, 10'db) which contains said inner cylindrical bearing surface (10cb, 10db) of said bearing member (10c, 10d), wherein an eccentric amount (E) of the center axial line (B) of said outer cylindrical bearing surface (10ca, 10da of said outer bearing portion (10'ca, 10'da) against the center axial line (A) of the inner cylindrical bearing surface (10cb, 10db) of the inner bearing portion (10'cb, 10'db) is adjustable. The rotating type scroll compressor as set forth in claim 2, wherein the excentric amount (E) of the center axial line (B) against the center axial line (A) being precisely adjustable corresponding to the relative rotation of the outer bearing portion (10'ca, 10'da) against the inner bearing portion (10'cb, 10'db). The rotating type scroll compressor as set forth in claim 3, wherein the eccentric amount (E) is adjustable corresponding to the relative rotation of the outer bearing portion (10'ca) against the inner bearing portion (10'cb), both portions being secured with bolts (56) for assembling. The rotating type scroll compressor as set forth in claim 3, wherein the bearing portions (10'da, 10'db) are rotatable with respect to each other, so that the sealing in the radial direction of the drive scroll member (14) and the follower scroll member (15) is improved due to the relative movement of the bearing portions (10'da, 10'db) caused by the load of the fluid while the apparatus is being operated. The rotating type scroll compressor as set forth in claim 1, wherein the second rotating shaft portion (53) has a restricted portion so that said second rotating shaft portion (53) restricts the movement in the axial direction of the follower scroll member (15), an intermediate pressure chamber (55) being formed between the end plate (19) of said follower scroll member (15) and said second rotating shaft portion (53), the intermediate pressure chamber (55) being connected to a compression space. The rotating type scroll compressor as set forth in claim 1, wherein the electric drive unit (2) is housed at a lower position of a closed shell (1) and the scroll compressing unit is housed at an upper position of said shell (1). The rotating type scroll compressor as set forth in claim 7, wherein the rotating shaft portions (18, 53) to which the radial force is applied have the form of a shaft member and a bearing shape.

Inventors: NOBORU YOSHINORI, SUGIMOTO KAZUYOSHI, NOBORU, YOSHINORI, SUGIMOTO, KAZUYOSHI
Applicants: SANYO ELECTRIC CO, SANYO ELECTRIC CO. LTD
Application year: 1995
Main classification: F04C18
IPC codes: F01C21, F04C29, F04C18, F04C27