SCROLL COMPRESSOR

Abstract: A scroll compressor comprises a housing, a frame, a fixed scroll and an orbiting scroll, arranged in said housing. The end plate of the orbiting scroll is slidably sandwiched, at its peripheral portion, between the fixed scroll and the frame. A back pressure chamber is formed between the back surface of the end plate of said orbiting scroll and said frame to press the orbiting scroll toward the fixed scroll under the action of a fluid pressure fed into said back pressure chamber. A plurality of radial ribs are formed on the back surface of the end plate of said orbiting scroll. These radial ribs extend from said bearing boss to the marginal side of the end plate of said orbiting scroll. These ribs are formed, at their marginal ends, with a seat which extends in the peripheral direction. The seat is formed with slots or holes which communicate the back pressure chamber with recessed portions formed between the radial ribs. The depths of the recessed portions are so adjusted as to position the center of gravity of the orbiting scroll on the central axis of the bearing.

Description: The present invention relates to a scroll compressor for use as a coolant compressor for e.g. a refrigerator, air conditioner or an air compressor, according to the preamble of claim 1. A machine of that kind is described in e.g. the Japanese Patent Application Laid-Open JP-A- 59-119.091 (corresponding to DE-A-3.345.073). A scroll compressor has been well known in the art. In general, the scroll compressor comprises a housing having a suction tube and a discharge tube; a frame fixedly mounted in said housing; a fixed scroll fixedly connected to said frame and having an end plate, a spiral wrap upstanding from said end plate in the form of an involute or a nearly involute shape, a discharge port formed near the center of said end plate and a suction port formed at the peripheral portion of said end plate; and an orbiting scroll revolutionally arranged in the frame and having an end plate and a spiral wrap upstanding from said end plate in the form of an involute or a nearly involute shape; in which the orbiting scroll and the fixed scroll are so arranged that their wraps are directed inward to make them mesh with each other. A rotation inhibiting mechanism, such as Oldham mechanism, is arranged between the orbiting scroll and the frame to prevent the orbiting scroll from rotating about its own axis. A bearing boss is formed on the back surface of the end plate of the orbiting scroll. A drive shaft driven by a motor has an eccentric shaft portion which is held in engagement with said bearing boss. By making revoluting motion of the eccentric shaft portion, the orbiting scroll produces an orbiting motion, without producing rotation thereof about its own axis. Thus, a gas contained in a confined space formed by the orbiting scroll and the fixed scroll is successively compressed and the compressed gas is discharged from the discharge port. Heretofore, the fixed scroll and the orbiting scroll have been made of cast iron, which has a relatively heavy weight. Accordingly, when the orbiting scroll is rotated at a high speed, the load on the bearing is increased owing to a centrifugal force acting on the orbiting scroll, that may result in lowing the reliability of the compressor. In order to enable the operation of the scroll compressor at higher speed, it has been heretofore proposed to decrease the weight of the orbiting scroll by making the orbiting scroll of a material having a low specific weight, such as aluminum alloy. Furthermore, it has been heretofore proposed to provide a construction in which asymmetrically arranged recesses are formed in the end plate of the orbiting scroll in order to locate the center of gravity of the orbiting scroll in alignment with the central axis of the bearing boss. Such a construction is shown in Japanese Patent Application Laid-Open No. Sho 58-110886, for example. Furthermore, in order to prevent the increase of the load applied to the compressor owing to compression of a fluid, such as a lubricating oil, which passes through the gap between the peripheral portion of the end plate of the orbiting scroll and the frame during revolution of the orbiting scroll, it has been proposed to provide a construction in which grooves are formed in the surface of the frame adjacent to the peripheral portion of the end plate or small grooves are formed in a part of the peripheral portion of the end plate, whereby the fluid can easily pass through the gap. An example of such construction is shown in Japanese Patent Application Laid-Open JP-A- 59-119091. According to the prior arts as described above, if the orbiting scroll is made of a cast iron, which has a heavy weight, the load on the bearing owing to the centrifugal force of the orbiting scroll during operation at a high speed is increased, with the result that the reliability of the compressor is lowered. On the other hand, if the orbiting scroll is made of a metallic material having a low specific weight, such as aluminum alloy, it is required to provide relatively wide gaps at the tip ends of the wraps of fixed scroll and the orbiting scroll, since the fixed scroll and the frame made of cast iron and the orbiting scroll made of aluminum alloy have substantial difference in coefficient of thermal expansion, etc. It is therefore required to provide tip seals at the tip ends of the wraps in order to seal the confined compressing space. In the construction heretofore proposed In which means is provided to locate the center of gravity of the orbiting scroll in alignment with the central axis of the bearing bass, such as shown in Japanese Patent Application JP-A-58-110886 etc., no consideration is given to decreasing the weight of the orbiting scroll, that is required to operate the compressor at a high speed. In the construction as shown in Japanese Patent Application Laid-Open JP-A-59-119091, means is provided to prevent the increase of the load owing to the compression of the fluid at the peripheral portion of the end plate of the orbiting scroll. However, no consideration is given to decreasing the weight of the orbiting scroll and locating the center of gravity of the orbiting scroll in substantial alignment with the central axis of the bearing boss, that is required to assure high speed operation of the compressor. US-A-4472120 discloses a scroll compressor for use as, eg, a refrigerant compressor, having reinforcing ribs on the rear side of the base plate. The ribs are provided to increase the rigidity of the base plate. It is also known from JP-A-60-233388 to provide a base plate suitable for a scroll compressor which has an eccentric center of mass. The present invention seeks to provide a scroll compressor in which the weight of the orbiting scroll is decreased, and/or the increase of the load owing to the compression of the fluid at the peripheral portion of the end plate of the orbiting scroll is prevented, and/or the center of gravity of the orbiting scroll is located in substantial alignment with the central axis of the bearing boss. In accordance with the present invention, there is provided a scroll compressor, having a housing, a frame arranged in said housing, a fixed scroll having an end plate, and a spiral wrap upstanding from a surface of said end plate, said end plate being connected at its peripheral portion to said frame, an orbiting scroll revolutionally arranged in opposed relation to said fixed scroll, having an end plate and a spiral wrap upstanding from a surface of said end plate, said end plate of said orbiting scroll being slidably sandwiched, at its peripheral portion, between the peripheral portion of said fixed scroll and said frame, said fixed scroll and said orbiting scroll being so arranged that their wraps are directed inward thereby to mesh with each other, a back pressure chamber formed between a back surface of the end plate of said orbiting scroll and said frame to press the orbiting scroll toward the fixed scroll under the action of a fluid pressure fed into said back pressure chamber, rotation inhibiting means arranged between said frame and said orbiting scroll to inhibit rotation of the orbiting scroll about its own axis whilst allowing orbiting revolution thereof, a bearing boss formed on the back surface of the end plate of said orbiting scroll, a drive shaft for driving said orbiting scroll, having an eccentric shaft portion arranged to engage with said bearing boss to cause the orbiting motion of said orbiting scroll; characterized by a plurality of radial ribs formed on the back surface of the end plate of said orbiting scroll, said plurality of ribs extending from said bearing boss to the marginal side of said end plate of said orbiting scroll, wherein said radial ribs form recessed portions therebetween which communicate an area outside the marginal side of the end plate of said orbiting scroll with said back pressure chamber. According to another embodiment of the present invention, there is provided a scroll compressor, having: a housing, a frame arranged in said housing, a fixed scroll having an end plate and a spiral wrap upstanding from a surface of said end plate, said end plate being connected at its peripheral portion to said frame, an orbiting scroll revolutionally arranged in opposed relation to said fixed scroll, having an end plate and a spiral wrap upstanding from a surface of said end plate, said end plate of said orbiting scroll being slidably sandwiched, at its peripheral portion, between the peripheral portion of said fixed scroll and said frame, said fixed scroll and said orbiting scroll being so arranged that their wraps are directed inward thereby to mesh with each other, a back pressure chamber formed between a back surface of the end plate of said orbiting scroll and said frame to press the orbiting scroll toward the fixed scroll under the action of a fluid pressure fed into said back pressure chamber, rotation inhibiting means arranged between said frame and said orbiting scroll to inhibit rotation of orbiting scroll about its own axis whilst allowing orbiting revolution thereof, a bearing boss formed on the back surface of the end plate of said orbiting scroll, a drive shaft for driving said orbiting scroll, having an eccentric shaft portion arranged to engage with said bearing boss to cause the orbiting motion of said orbiting scroll; characterised by a plurality of radial ribs formed on the back surface of the end plate of said orbiting scroll, said plurality of ribs extending from said bearing boss to the marginal side of said end plate of said orbiting scroll, wherein said ribs are formed, at their marginal ends, with a seat which extends in the peripheral direction of said orbiting scroll, wherein said seat is formed with slots or holes which communicate the area outside of the seat with the recessed portions formed between said radial ribs and wherein said recessed portions communicate with said back pressure chamber. According to a further embodiment of the invention, the depths of the recessed portions formed between the radial ribs are so adjusted that the center of gravity of said orbiting scroll is positioned substantially on the central axis of said bearing boss. According to a further embodiment of the invention, the width of said seat is so adjusted that the center of gravity of said orbiting scroll is positioned substantially on the central axis of said bearing boss. According to the present invention as described above, the radial ribs extend substantially at right angle to the spiral wrap of the orbiting scroll, whereby a relatively rigid construction of the orbiting scroll is obtained, so that the thickness of the end plate can be reduced and thus the weight of the orbiting scroll can be decreased. The center of gravity of the orbiting scroll can be located in substantial alignment with the central axis of the bearing boss, by adjusting the depths of the recesses formed between the radial ribs or adjusting the width of the seat formed at the peripheral portion of the end plate. As the result, the effect of the centrifugal force of the orbiting scroll can be reduced and the vibration of the scroll compressor can be reduced, so that the compressor can be operated at higher speed. Furthermore, the recesses formed between the radial ribs constitute lubricant oil passages which communicate the marginal side of the end plate of the orbiting scroll with the back pressure chamber, so that the compression of the lubricant oil is prevented even where the marginal side of the peripheral portion of the end plate of the orbiting scroll comes close to an inside surface opposite thereto of the frame during revolution and thus the power consumption of the compressor can be reduced. The accompanying drawings 1-12,16 and 17 illustrate the embodiments of the present invention. Fig. 1 is a longitudinal sectional view of one embodiment of the scroll compressor according to the present invention; Fig. 2 is a plan view of an example of the orbiting scroll for the scroll compressor according to the present invention, as viewed from the wrap side; Fig. 3 is a plan view of the orbiting scroll shown in Fig. 2, as viewed from the back side thereof ; Fig. 4 is a sectional view taken along a line A-O-A in Fig. 2; Fig. 5 is an enlarged sectional view, showing the relation between the orbiting scroll and the fixed scroll of the embodiment shown in Fig. 1; Fig. 6 shows another example of the orbiting scroll for the scroll compressor according to the present invention; Fig. 7 shows a further example of the orbiting scroll for the scroll compressor according to the present invention; Fig. 8 is a partial side view of the orbiting scroll shown in Fig. 7; Fig. 9 is a plan view of another embodiment of the orbiting scroll according to the present invention, as viewed from the wrap side; Fig. 10 is a plan view of the orbiting scroll shown in Fig. 9, as viewed from the back side thereof; Fig. 11 is a sectional view taken along a line A-O-A in Fig. 9; Fig. 12 is a partial enlarged sectional view showing the orbiting scroll shown in Figs. 9, 10 and 11, as combined with the fixed scroll and the frame; Fig. 13 is a plan view of orbiting scroll not according to the present invention, as viewed from the wrap side; Fig. 14 is a plan view of the orbiting scroll as shown in Fig. 13, as viewed from the back side thereof; Fig. 15 is a sectional view taken along a line A-O-A in Fig. 13; Fig. 16 is a plan view of a further embodiment of the orbiting scroll according to the present invention, as viewed from the back side thereof; and Fig. 17 is a partial side view of the orbiting scroll shown in Fig. 16. Now, the present invention will be explained, with reference to the embodiments illustrated in the accompanying drawings. Firstly, the embodiment illustrated in Figs. 1-5 will be explained. Fig. 1 is a longitudinal sectional view showing the embodiment of the scroll compressor according to the present invention. The scroll compressor shown in Fig. 1 includes an orbiting scroll 1 having a spiral wrap 1a and a fixed scroll 2 having a similar spiral wrap 2a. The orbiting scroll and the fixed scroll 2 are arranged in meshing relation with each other, thereby constituting a compressing part. The fixed scroll 2 is connected with a frame 3 and fixedly mounted in a sealed housing 18. The orbiting scroll 1 has an end plate, which is slidably sandwiched at its peripheral portion between a surface 2c of an end plate 2b of said fixed scroll 2 and a surface 3b of the frame 3, with small gaps (not shown) being held therebetween, as shown in Fig. 5. A bearing boss 6 is formed on the back side of the end plate of the orbiting scroll. A drive shaft 10 has an eccentric shaft portion, namely, a crank pin 10a, which is in bearing engagement with said boss 6. A motor 11, which is mounted in the housing 18, serves to rotate the drive shaft 10, whereby the orbiting scroll 1 produces an orbiting motion relatively to the fixed scroll 2, while the rotation of the orbiting scroll about its own axis is inhibited under the action of the Oldham mechanism 8. As the orbiting scroll 1 produces the orbiting motion relatively to the fixed scroll 2, a gas is introduced through a suction pipe 12 into a compressing chamber formed between the wraps of these scrolls and gradually compressed as the volume of the compressing chamber is reduced. The compressed gas is discharged through the central discharge port 2d of the fixed scroll into an upper discharge chamber 13 and then the gas is passed through a motor chamber 14, positioned underside of the compressor, and discharged through a discharge pipe 15 to the outside of the compressor. During operation, the gas at an intermediate pressure between the suction pressure and the discharge pressure is introduced into the back pressure chamber 7 enclosed by the orbiting scroll and the frame 7, and such intermediate pressure acts on the back surface of the orbiting scroll 1, thereby generating a pressing force to press the orbiting scroll 1 toward the fixed scroll 2 in axial direction. Preferably, the introduction of such intermediate pressure is effected by passing the gas, which is under compressing process between the wraps of the both scrolls, into the back pressure chamber 7 through small holes (not shown) formed through the end plate of the orbiting scroll. During operation, the lubricant oil is fed from an oil reservoir 16 at the bottom in the sealed container 18, through a feeding pipe 17 and a feeding bore 20 formed in the drive shaft 10, to bearings for the drive shaft 10 supported by the frame 3 and to a bearing inserted in the boss 6 of the orbiting scroll. The lubricant oil also serves to lubricate the Oldham mechanism 8 and, furthermore, it passes from the back pressure chamber 7 through a space 4 formed between a marginal side 1f of the end plate of the orbiting scroll 1 and an inner side 3a opposite thereto of the frame 3 into the compressing chamber between the both scrolls, thereby lubricating the sliding surfaces of the orbiting scroll confronting the frame 2 and the fixed scroll 2. Then, the lubricant oil is discharged, together with the gas, into the discharge chamber 13. The gas discharged with the oil into the discharge chamber 13 is passed through the motor chamber 14 and a part of the lubricant oil is returned into the reservoir 16 and the other part of the lubricant oil is discharged, together with the gas, through the discharge pipe 15 to the outside of the compressor. The detailed construction of the orbiting scroll 1 of the scroll compressor according to this embodiment is shown in Fig. 2, Fig. 3 and Fig. 4. The partial enlarged view of the orbiting scroll 1 combined with the fixed scroll 2 and the frame 3 is shown in Fig. 5. As shown in Fig. 2, Fig. 3 and Fig. 4, the end plate 1b of the orbiting scroll 1 is formed with radial ribs 1c on the surface opposite to the surface on which the spiral wrap 1a is formed. The radial ribs 1c include a plurality of ribs which radially extend from the boss 6, which receives the eccentric shaft portion, namely, the crankpin 10a of the drive shaft 10, to the peripheral portion of the end plate 1b. Some of the radial ribs are arranged, in pairs, to form Oldham key ways. Referring to Fig. 4, T indicates the sum of the thickness t of the end plate and the height h of the radial rib 1c (namely, the depth of the recess 1e formed between the radial ribs), which is constant. As shown in Fig. 5, the end plate of the orbiting scroll is slidably sandwiched between the surface 3b of the frame 3 and the surface 2c of the end plate 2b of the fixed scroll, with small gaps (not shown) being held between the top surface of the radial rib 1c and the surface 3b of the frame 3. As shown in Fig. 2, the plurality of radial ribs 1c extend at substantially right angle to the spiral wrap 1a, thereby forming a rigid construction of the orbiting scroll, so that the thickness of the end plate 1b can be reduced, as compared to the conventional construction and thus the weight of the orbiting scroll can be reduced. The recesses 1e formed between the radial ribs 1c extend to the marginal side 1f of the end plate 1b and constitute lubricant oil passages which communicate the area outside of the marginal side 1f of the orbiting scroll (the space 4 as hereinbefore described) with the back pressure chamber 7. Accordingly, the surface area of the marginal side 1f of the end plate is reduced, and there are formed passages through which the lubricating oil can easily pass even when the marginal side 1f of the end plate comes near the inside surface 3a of the frame 3, as shown in Fig. 5. Therefore, the lubricant oil is not compressed by the marginal side of the end plate and, thus, the increase of load owing to the compression of the lubricant oil is avoided. In the above construction, it is possible to locate the center of gravity of the orbiting scroll 1, as viewed in the plan view, in alignment with the central axis of the bearing boss 6, by adjusting the thicknesses of the end plate 1b at the positions between the radial ribs 1c, namely, the depths of the recesses 1e formed between the radial ribs, although not particularly illustrated in the drawings. Fig. 6 illustrates an example of the orbiting scroll in which the surface area of the peripheral portion of the end plate of the orbiting scroll to contact with the surface 3b of the frame 3 is increased, with the object of decreasing the surface pressure at which the end plate of the orbiting scroll is pressed against the surface 3b of the frame 3 under the action of the gas pressure at the time of starting of the compressor. In this example, a seat 5 having a height equal to that of the radial rib 1c is formed on the whole circumference of the end plate and said seat is partly cut to form small slots 5a, which communicate the area outside of the seat 5 with the respective recesses 1e. Fig. 7 and Fig. 8 illustrate another example, in which small holes 5b are formed in the seat 5 at several parts thereof, in place of the slots as shown in Fig. 6. The small holes 5b communicate the area outside of the seat 5 with the respective recesses 1e. Now, several examples of the construction in which the center of gravity of the orbiting scroll is adjusted by adjusting the width of the circumferential seat 5 formed on the end plate, with reference to Figs. 9-17. In the example shown in Figs. 9, 10 and 11, the radial ribs 1c are formed on the side of the the end plate 1b of the orbiting scroll 1 opposite to the side on which the wrap 1a is formed. The radial ribs 1c are formed with the bearing boss 6. The end plate 1b has a constant thickness at the portions between these ribs 1c and recesses 1e are formed between the ribs 1c. The radial ribs 1c are arranged substantially at right angle to the wrap 1a, so that high rigidity of the orbiting scroll 1 is obtained, irrespectively of the thin thickness of the end plate 1b, and thus the weight of the orbiting scroll 1 can be reduced. The forward end portion of the radial rib 1c is integrally connected with the seat 5 which extends in circumferential direction on the peripheral portion of the end plate 1b. The seat 5 forms a contact surface which contacts with the surface 3b of the frame 3. The center of gravity of the orbiting scroll 1 can be located in alignment with the central axis of the boss 6, by adjusting the width (consequently, the contact area) of the seat 5. In order to avoid the power loss which may be caused by agitation and/or compression of the lubricant oil in the space 4 (shown in Fig. 12) between the marginal side 1f of the end plate of the orbiting scroll and the inside surface 3a of the frame 3, the seat 5 is formed with cut portions 5a which communicate the above-mentioned space 4 outside of the marginal side of the end plate of the orbiting scroll 1 with the recesses 1e formed between the radial ribs, whereby the area of said seat 5 on the peripheral portion of the end plate 1b of the orbiting scroll is reduced and, furthermore, lubricant oil passages are formed to communicate the space 4 outside of the marginal side 1f of the end pate of the orbiting scroll with the back pressure chamber 7 through said cut portions 5a and said recesses 1e. The sum T of the height h of the radial rib 1c (which is equal to the height of the seat 5) plus the thickness t of the end plate at the positions between said radial ribs 1c is determined to be slightly smaller than the distance between the surface 2c of the fixed scroll 2 and the surface 3b of the frame 3, so that the end plate of the orbiting scroll is sandwiched between the above-mentioned surfaces 2c and 3b, with small gaps therebetween. Fig. 13, Fig. 14 and Fig. 15 illustrate an orbiting scroll in which the contact seat 5 which contacts with the frame 3, as shown in Figs. 9, 10 and 11, is formed as a continuous part extending in peripheral direction, thereby further increasing the rigidity of the orbiting scroll. As there is no communication between the recessed portions 1e and the back pressure chamber 7, Figs. 13, 14 and 15 are not embodiments of the present invention. Fig. 16 and Fig. 17 illustrate an embodiment in which the seat 5 is formed with through-holes 5b, which constitute passages of the lubricant oil for communicating the space 4 outside of the marginal side of the end plate of the orbiting scroll 1 with the back pressure chamber 7, as in the embodiment shown in Figs. 9, 10 and 11. Now, the explanation will be given to the technical advantages to be obtained from the embodiments of the present invention as described above. According to the present invention, the weight of the orbiting scroll 1 is reduced by decreasing the thickness of the end plate 1b, throughout the whole excluding the ribs 1c and the seat 5. Accordingly, the centrifugal force owing to the weight of the orbiting scroll itself during the operation of the compressor at a high speed can be minimized, so that the bearing load can be reduced, with the result that the reliability of the compressor is improved. Although the thickness of the end plate is decreased, the rigidity of the orbiting scroll is not lowered, owing to the existence of the radial ribs 1c which extend at right angle to the spiral wrap 1a. In the embodiments as shown in Figs. 2, 3 and 4, Fig. 6 and Figs. 7 and 8, the center of gravity of the orbiting scroll 1 is adjusted by adjusting the depths of the recesses formed between the radial ribs 1c, so that said center of gravity is located in alignment with the central axis of the boss 6. In the embodiments as shown in Figs. 9, 10 and 11, Figs. 13, 14 and 15 and Figs. 16 and 17, the same adjustment of the center of gravity of the orbiting scroll is effected by adjusting the contacting area (width) of the contact seat 5. By the adjustment of the center of gravity of the orbiting scroll, the occurrence of an unstable revolution of the orbiting scroll 1 can be avoided, whereby the occurrence of non-uniform contact between the relatively sliding parts, such as between the drive shaft and the bearing, can be avoided, and the generation of vibration and noise can be reduced. Even when the space 4 is narrowered by approaching of the marginal side 1f of the end plate of the orbiting scroll 1 to the inside surface 3a of the frame 3, as shown in Fig. 5 or Fig. 12 the lubricant oil can flow out of said space, through the recesses 1b formed between the radial ribs 1c, in the embodiment shown in Figs. 2, 3 and 4, or the recesses 1e between the radial ribs and the cut portions 5a or the holes 5b, in the embodiments shown in Fig. 6, Figs. 7 and 8, Figs. 9, 10 and 11 and Figs. 16 and 17. Accordingly, the increase of the power consumption, which may be caused by agitation and/or compression of the lubricant oil, can be avoided. A further difference is noted between the conventional scroll compressor and that of the present invention. In general, the orbiting scroll of the scroll compressor tends to move away from the fixed scroll under the action of the thrust force caused by the pressure of the compressed gas during operation of the scroll compressor. According to the conventional type scroll compressor, the orbiting scroll tending to move away from the fixed scroll by said thrust force is supported by the frame, while according to the present invention the fluid pressure introduced into the back pressure chamber acts on the back side of the end plate of the orbiting scroll, thereby pressing the orbiting scroll toward the fixed scroll against the said thrust force applied to the orbiting scroll. Therefore, in the scroll compressor according to the present invention, it is not required to support the orbiting scroll by the frame during operation of the compressor, and it is only required to support the orbiting scroll by the frame only at the time of starting the compressor or the time when the compressor is stopped where the gas is at a low pressure. Thus, the provision of a small supporting area, such as the seat 5 or the ribs 1c, is enough to support the the orbiting scroll on the frame at the time of starting or stopping the compressor. It is not always necessary to form an annular portion 1c₁, which connects together the inner ends of the radial ribs 1c, and the radial portions of the radial ribs 1c may be so constructed that they extend directly from the bearing boss 6 in radial directions. It will be understood from the above description that the present invention provides several technical advantages as enumerated below. The weight of the orbiting scroll can be considerably reduced, so that the centrifugal force caused by the orbiting scroll itself during operation of the compressor at a high speed is lowered and, consequently, the load on thee bearing portions is reduced, with the result that the reliability of the scroll compressor is improved. In the scroll compressor according to the present invention, the weight of the orbiting scroll can be reduced owing to the construction and the shape of the orbiting scroll. Accordingly, the reduction of the weight of the orbiting scroll is possible even if the orbiting scroll is made of cast iron, and thus it is possible to remove the hereinbefore-mentioned problem which may be caused owing to the difference in coefficient of thermal expansion between the fixed scroll and the orbiting scroll if the orbiting scroll is made of aluminum alloy. Furthermore, it is possible to locate the center of gravity of the orbiting scroll on the central axis of the bearing boss by adjusting the thicknesses of the end plate at the areas between the radial ribs, namely, the depths of the recesses formed between the radial ribs or adjusting the width of the contact seat formed on the peripheral portion of the end plate, and thus, the occurrence of unstable revolution of the orbiting scroll is avoided, so that the occurrence of non-uniform contact between the relatively sliding parts and the generation of noise are reduced. The lubricant oil in the space between the marginal side of the end plate of the orbiting scroll and the inside surface of the frame can flow out of said space through the recesses formed between the radial ribs when the marginal side of the end plate comes close to the inside surface of the frame. Accordingly, the increase of load which may be caused by the compression of the lubricant oil in said space can be avoided.

Claims: A scroll compressor, having a housing (18), a frame (3) arranged in said housing (18), a fixed scroll (2) having an end plate, and a spiral wrap (2a) upstanding from a surface of said end plate, said end plate being connected at its peripheral portion to said frame (3), an orbiting scroll (1) revolutionally arranged in opposed relation to said fixed scroll (2), having an end plate and a spiral wrap (1a) upstanding from a surface of said end plate, said end plate of said orbiting scroll (1) being slidably sandwiched, at its peripheral portion, between the peripheral portion of said fixed scroll (2) and said frame (3), said fixed scroll (2) and said orbiting scroll (1) being so arranged that their wraps (1a, 2a) are directed inward thereby to mesh with each other, a back pressure chamber (7) formed between a back surface of the end plate of said orbiting scroll (1) and said frame (3) to press the orbiting scroll (1) toward the fixed scroll (2) under the action of a fluid pressure fed into said back pressure chamber (7), rotation inhibiting means (8) arranged between said frame (3) and said orbiting scroll (1) to inhibit rotation of the orbiting scroll (1) about its own axis whilst allowing orbiting revolution thereof, a bearing boss (6) formed on the back surface of the end plate of said orbiting scroll (1), a drive shaft (10) for driving said orbiting scroll (1), having an eccentric shaft portion (10a) arranged to engage with said bearing boss (6) to cause the orbiting motion of said orbiting scroll (1); characterized by a plurality of radial ribs (1c) formed on the back surface of the end plate of said orbiting scroll (1), said plurality of ribs (1c) extending from said bearing boss (6) to the marginal side of said end plate of said orbiting scroll (10), wherein said radial ribs (1c) form recessed portions (1e) therebetween which communicate an area outside the marginal side of the end plate of said orbiting scroll (1) with said back pressure chamber (7). A scroll compressor, having: a housing (18), a frame (3) arranged in said housing (18), a fixed scroll (2) having an end plate and a spiral wrap (2a) upstanding from a surface of said end plate, said end plate being connected at its peripheral portion to said frame (3), an orbiting scroll (1) revolutionally arranged in opposed relation to said fixed scroll (2), having an end plate and a spiral wrap (1a) upstanding from a surface of said end plate, said end plate of said orbiting scroll (1) being slidably sandwiched, at its peripheral portion, between the peripheral portion of said fixed scroll (10) and said frame (3), said fixed scroll (2) and said orbiting scroll (1) being so arranged that their wraps (1a, 2a) are directed inward thereby to mesh with each other, a back pressure chamber (7) formed between a back surface of the end plate of said orbiting scroll (1) and said frame (3) to press the orbiting scroll (1) toward the fixed scroll (2) under the action of a fluid pressure fed into said back pressure chamber (7), rotation inhibiting means (8) arranged between said frame (3) and said orbiting scroll (1) to inhibit rotation of the orbiting scroll (1) about its own axis whilst allowing orbiting revolution thereof, a bearing boss (6) formed on the back surface of the end plate of said orbiting scroll (1), a drive shaft for driving said orbiting scroll, having an eccentric shaft portion (10a) arranged to engage with said bearing boss (6) to cause the orbiting motion of said orbiting scroll (1); characterised by a plurality of radial ribs (1c) formed on the back surface of the end plate of said orbiting scroll (1), said plurality of ribs (1c) extending from said bearing boss (6) to the marginal side of said end plate of said orbiting scroll (1), wherein said ribs (1c) are formed, at their marginal ends, with a seat (5) which extends in the peripheral direction of said orbiting scroll, wherein said seat (5) is formed with slots (5a) or holes (5b) which communicate the area outside of the seat (5) with the recessed portions (1e) formed between said radial ribs (1c) and wherein said recessed portions (1e) communicate with said back pressure chamber (7). A scroll compressor according to any preceding claim, wherein the depths of the recessed portions (1e) formed between the radial ribs (1c) are such that the center of gravity of said orbiting scroll (1) is positioned substantially on the central axis of said bearing boss (6). A scroll compressor according to claim 2, wherein the width of said seat (5) is such that the center of gravity of said orbiting scroll (1) is positioned substantially on the center axis of said bearing boss (6).

Inventors: AMATA, ATUSHI, MIZUNO, TAKAO, UCHIKAWA, NAOSHI
Applicants: HITACHI, LTD.
Application year: 1991
Main classification: F04C18
IPC codes: F04C23, F04C18