Scroll compressor

Abstract: The scroll compressor has a fixed scroll (1), a rotating scroll (2), a compliant frame (3) axially supporting the rotating scroll (2) and radially supporting a main shaft (4) for driving the rotating scroll (2) and a guide frame (4) fixed to a hermetically sealed vessel (10) and radially supporting the compliant frame (3). The rotating scroll (2) is slidable in the axial direction by sliding of the compliant frame (3) on the guide frame (4). A space (15f) is formed between the frame (3,4). The pressure in the space (15f) is higher than the suction pressure and at most the same as the discharge pressure. Thus, relief of the rotating scroll (2) is avoidable to quickly and constantly realize a state of normal operation.

Description: The present invention relates to a refrigerant compressor used for a refrigerating machine. Figure 8 is a cross-sectional view in a longitudinal direction of a scroll compressor shown in Japanese Patent Application JP9-268579 as background art. A fixed scroll 1 has its outer peripheral part fastened by bolts (not shown) to a guide frame 15. A spiral turbine 1b is formed on one surface (a lower side in Figure 8) of a seat 1a, and a pair of Oldham's coupling grooves 1c are formed to be substantially linear in an outer peripheral part of the seat, with which Oldham's coupling grooves 1c a pair of fixed projections 9c of an Oldham's coupling 9 are engaged so as to be reciprocally slidable. A suction tube 10a is press-fitted to a hermetically sealed vessel by penetrating from a side of the fixed scroll 1 (a right side in Figure 8). A rotating scroll 2 has, on one surface of a seat 2a (an upper side in Figure 8), a spiral turbine 2b having substantially the same shape as that of the spiral turbine 1b of the fixed scroll 1. On a central portion of an opposite surface (a lower side in Figure 8) to that of the spiral turbine 2b of the seal 2a, a boss 2f having a hollow cylindrical shape is formed, and on an inner side surface of the boss 2f, a bearing 2c is formed. Further, on an outer periphery in the same surface as that of the boss 2f, a thrust face 2d which is slidably in contact with a thrust bearing 3a of a compliant frame 3 is formed. In an outer peripheral part of the seat 2a of the rotating scroll 2, a pair of Oldham's coupling grooves 2e are formed to be substantially linear, with a phase difference of about 90° from the Oldham's coupling groove 1c of the fixed scroll, to which Oldham's coupling groove 2e a pair of rotating projections 9a of the Oldham's coupling 9 are engaged reciprocally slidable. In a central portion of the compliant frame 3, a main bearing 3c and an auxiliary main bearing 3h, both for radially supporting a main shaft 4 rotatably driven by a motor 7 are formed. Although an outer periphery 15g of the guide frame 15 is fixed to the hermetically sealed vessel by an interference shrink fit, welding or the like, a flow path for introducing a refrigerant gas having a high pressure discharged from a discharge port 1f of the fixed scroll 1 from the guide frame 15 to a discharge tube 10b provided on the motor side (lower side in Figure 8) is maintained. An upper bore surface 15a is formed on the fixed scroll side in an inner side surface of the guide frame 15 (upper side in Figure 8) and fitted and engaged with an upper cylindrical surface 3d formed in an outer periphery surface of the compliant frame 3. On the other hand, a lower bore surface 15b is formed on the motor side in an inner side surface of the guide frame 15 (lower side in Figure 8) and fitted and engaged with a lower cylindrical surface 3e formed on an outer peripheral surface of the compliant frame 3. In an inner side surface of the guide frame 15, two sealing grooves for accommodating a sealing material are formed, and an upper seal 16a and a lower seal 16b are fitted and engaged with these sealing grooves. A space 15f is delimited by these two seals 16a, 16b, the inner side surface of the guide frame 15 and the outer side surface of the compliant frame 3 is connected to a space 2h around the boss 2f through a pressure equalizing aperture 3i formed in the compliant frame 3. The upper seal 16a and the lower seal 16b are not necessarily indispensable and can be omitted if sealing is possible in a micro-clearance among engaging portions. A space 2i around the outer periphery of the seat 2a, which is in the outer peripheral side of the thrust bearing 3a surrounded by the seat 2a of the rotating scroll and the compliant frame 3 in the vertical directions, is connected to a suction chamber 1g in the vicinity of an end of the spiral turbine to have an atmosphere of suction gas. At the end of the main shaft 4 on the rotating scroll side (upper side in Figure 8), an orbit shaft body 4b which is rotatably engaged with the bearing 2c of the rotating scroll 2 is formed. To the lower side of the main shaft, a main shaft balancer 4e is fixed by an interference shrinkage fit, and a main shaft body 4c which is rotatably engaged with the main bearing 3c and the auxiliary main bearing 3h both of the compliant frame 3 is formed beneath the main shaft balancer 4e. On the other end of the main shaft, a subshaft body 4d rotatably engaged with a subbearing 6a of a subframe 6 is formed. Between the subshaft body 4d and the above-mentioned main shaft body 4c, a rotor 8 of the motor 7 is fixed by an interference shrinkage fit. An upper balancer 8a is formed on an upper end of the rotor 8, and a lower balancer 8b is fastened to a lower end of the rotor, whereby a static balance and a dynamic balance are maintained by the above-mentioned main shaft balancer 4e and these three balancers. An oil pipe 4f is press-fitted to a lower end of the main shaft 4 for sucking up a refrigerating oil 10 accumulated in a bottom of the hermetically sealed vessel 10. A glass terminal 10f is attached to a side surface of the hermetically sealed vessel 10, to which glass terminal a lead wire from a stator of the motor 7 is connected. Standard operation of the conventional scroll compressor will be described. In normal operation, because an area 10d of the hermetically sealed vessel 10 has a high pressure under an atmosphere of discharge gas, the refrigerating oil 10e in the bottom of the hermetically sealed vessel 10 is introduced from a high-pressure lubrication hole 4g formed in the main shaft 4 by penetrating in the axial direction to a space 2g in the boss 2f. This high-pressure oil is depressurized by the bearing 2c so as to have an intermediate pressure and flows toward the space 2h around the boss 2h. The refrigerating oil having an intermediate pressure flows through the pressure equalizing aperture 3i to the space 15f and is released to the space 2i around the outer periphery of the seat 2a having a low pressure through an intermediate pressure adjusting valve or the like. Although downward force as much as the sum of force caused by the intermediate pressure in the space 2h and a pressure from the rotating scroll 2 through the thrust bearing 3a effects on the compliant frame 3, upward force as much as the sum of force caused by the intermediate pressure in the space 15f and a force caused by the high pressure effecting on a portion exposed to the atmosphere of high pressure in the lower end surface produces force larger than the downward force in the normal operation. Accordingly, in the compliant frame 3, the upper cylindrical surface 3d is guided by the upper bore surface 15a of the guide frame and the lower cylindrical surface 3e is guided by the lower bore surface 15b of the guide frame 15, whereby the compliant frame 3 floats on the side of the fixed scroll in the upward direction in Figure 8. Also the rotating scroll 2 pushed to the compliant frame 3 through the trust bearing 3a floats in the upward direction, wherein tops and bottom of the rotating scroll 2 are slidably in contact with bottom and tops of the fixed scroll 1 respectively. At a time of starting up and liquid compression, a load by gas in the thrust direction acting on the rotating scroll 2 is increased to strongly push down the compliant frame 3 on the reverse side of the fixed scroll through the rotating scroll 2 and the thrust bearing 3a. Therefore, a relatively large gap is produced between the tops and the bottom of the rotating scroll 2 and the bottom and the tops of the fixed scroll 1 so as to be able to avoid an abnormal pressure increase in a compression chamber. The amount of relief is determined by a distance between a contact face 3q of the compliant frame 3 and a contact face 15h of the guide frame 15. Incidentally, although a part of or all of overturning moment generated in the rotating scroll 2 is transmitted through the thrust bearing 3a, resultant force of a load received from the main shaft bearing 3c and a reaction to the load, namely coupled force of reaction force received from the guide frame 15 through the upper cylindrical surface 3d and reaction force received from the guide frame 15 through the lower cylindrical surface 3e, acts to compensate the overturning moment, whereby excellent stability in follow-up operation and also in relief operation is obtainable. In the conventional scroll compressor of which compliant frame was movable in the axial direction by maintaining its own balance in terms of the moment, i.e. so-called compliant frame type scroll compressor of the background art, the intermediate pressure in the space 2h around the boss 2f leaked to the space 2i around outer periphery of the seat 2a when the rotating scroll 2 flapped on the thrust bearing 3a of the compliant frame 3 owing to a tiny outer disturbance such as a variation of a condition of operating pressure and suction of liquid refrigerant. Consequently, the intermediate pressure in the space 15f leaked to the space 2i having an atmosphere of low pressure through the pressure equalizing aperture 3i. Accordingly, force for lifting the compliant frame 3 up on the side of the fixed scroll (upward direction in Figure 8) was decreased to thereby relieve the compliant frame 3 on the reverse side of the fixed scroll (downward direction in Figure 8) along with the rotating scroll 2. In other words, there was unstability in that the rotating scroll 2 was easily relieved by a tiny outer disturbance. Further, in the conventional scroll compressor, a degree of freedom in setting a working area of the space 15f, i.e. an area having the intermediate pressure, which was a major factor of lifting up the compliant frame 3 on the fixed scroll side (upward direction in Figure 8), was less because it should have be restricted by a working area of the space 2h, i.e. the same space having the intermediate pressure as that of the space. Further, in the conventional scroll compressor, the intermediate pressure in the space 15f, which was a major factor of lifting the compliant frame 3 in the direction of the fixed scroll (upward direction in Figure 8) just after starting up, was generated such that an inner pressure of the hermetically sealed vessel 10 was increased and the refrigerating oil 10e having a high pressure was choked by the bearing and flowed into the space 15f. Therefore, there was a time lag until the intermediate pressure in the space 15f started to rise. Accordingly, there was a problem that it took a time until the compliant frame 3 floated for the normal operation, in other words, a considerable amount of time was necessary for starting up. Further, in the conventional scroll compressor, there were problems that the spiral turbines 1b and 2b may have been destroyed and that the bearing 2c and the main bearing 3c seized by an excessive load as a result of an abnormal pressure rise in the compression chamber, formed by the spiral turbine 1b of the fixed scroll 1 and the spiral turbine 2b of the rotating scroll 2, caused by a liquid compression when an amount of play in the axial direction of the compliant frame 3 was small enough to allow a liquid refrigerant to suck in a running state. Further, in the conventional scroll compressor, there were problems that an extremely long period was necessary to realize normal operation by making the compliant frame 3 float or that starting-up was impossible at worst because, when the amount of play in the axial direction of the compliant frame 3 was large, the compliant frame 3 was maximally relieved at the time of starting up so that the rotating scroll 2 was apart from the fixed scroll 1 to the maximum extent in the axial direction; the rotating scroll 2 arbitrarily rotates with effecting less compressing operation; and therefore the inner pressure of the hermetically sealed vessel is scarcely increased. US-A-4 552 518 (= FR-A-2 559 847) discloses a scroll compressor in accordance with the preamble of claim 1. It would be desirable to be able to solve the above-mentioned problems inherent in the conventional technique and to improve unstability that the compliant frame 3 and the rotating scroll 2 are easily relieved by flapping of the rotating scroll 2 caused by a tiny outer disturbance. It would also be desirable to be able to provide a sufficient degree of freedom for setting a working area of the space 15f. It would also be desirable to be able to provide a compressor having no possibility of destroying spiral turbines for compression and bearings are not seized. It would also be desirable to be able to provide a compressor having an excellent starting-up property. It would also be desirable to be able to provide a compressor in which loss by sliding of a rotating scroll is reduced and stable lubrication to bearings is possible. The present invention provides a scroll compressor as set forth in claim 1. A scroll compressor according to the invention comprises a fixed scroll having a spiral turbine and a rotating scroll having a spiral turbine, which spiral turbines are engaged each other to form a compression chamber between these, which fixed scroll and rotating scroll are located in a hermetically sealed vessel. A compliant frame supports the rotating scroll in its axial direction and supports a main shaft for driving the rotating scroll in directions of its radiuses. A guide frame supports the compliant frame in the directions of the radiuses, which guide frame is fixed to the hermetically sealed vessel. The rotating scroll is movable in the axial direction by a sliding motion of the compliant frame with respect to the guide frame in the axial direction. A space is formed between the compliant frame and the guide frame, and a pressure in the space is higher than a suction pressure and is the same as a discharge pressure or less. In one embodiment a space around a boss having a pressure higher than the suction pressure and the same as the discharge pressure or less is formed between the rotating scroll and the compliant frame. In one embodiment the space around the boss and the space between the frames are connected; and a fluid is allowed to flow from the space around the boss to the other space. In another embodiment a bottom portion of the hermetically sealed vessel accumulating a refrigerating oil has a high pressure of which the magnitude is around that of the discharge pressure; the space around the boss is located in a middle of an oil supplying route and the space between the frames is connected to an area having a low pressure through a pressure adjusting device. In another embodiment a pressure in the space between the frames and a pressure in the space around boss are independent each other. In another embodiment a bottom portion of the hermetically sealed vessel accumulating a refrigerating oil has a high pressure of which the magnitude is around that of the discharge pressure; the space around the boss is located in a middle of an oil supplying route and the space around boss is connected to an area having a low pressure through a pressure adjusting device. In another embodiment the space between the frames is connected to the compression chamber under compressing operation to make a pressure in the space higher than the suction pressure and the same as the discharge pressure or less. Preferably, the maximum movable distance of the rotating scroll with respect to the guide frame in the axial direction is 30 µm or more and 300 µm or less. A more complete appreciation of the invention and many of the attendant advantages thereof will be readily obtained as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein: Figure 1 is a longitudinal cross-sectional view of a scroll compressor according to Embodiment 1 of the present invention; Figure 2 schematically shows an important part in longitudinal cross-section according to Embodiment 1; Figure 3a schematically shows one extreme of the maximum movable distance in an axial direction according to Embodiment 1; Figure 3b schematically shows the other extreme of the maximum movable distance in an axial direction according to Embodiment 1; Figure 4 is a diagram for explaining a rise of an inner pressure when a liquid refrigerant is compressed; Figure 5 is a diagram for explaining a starting-up property; Figure 6 schematically shows an important part in longitudinal cross-section of a scroll compressor according to Embodiment 2 of the present invention; Figure 7 schematically shows an important part in longitudinal cross-section of a scroll compressor according to Embodiment 3 of the present invention; and Figure 8 is a longitudinal cross-sectional view for showing a conventional scroll compressor. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A detailed explanation will be given of preferred embodiments of the present invention in reference to Figures 1 through 7 as follows, wherein the same numerical references are used for the same or the similar portions, avoiding repeated description of such portions. EMBODIMENT 1 Embodiment 1 will be described in reference of Figures 1 through 5. A fixed scroll 1 has its outer peripheral part fastened by bolts (not shown) to a guide frame 15. One surface of a seat 1a (lower side in Figure 1) is formed with a spiral turbine 1b and outer peripheral part of the seat 1a is formed with a pair of Oldham's coupling grooves 1c substantially in line. A pair of fixed projections 9c of an Oldham's coupling 9 are engaged with the Oldham's coupling grooves 1c in a reciprocally slidable manner. Further, a suction tube 10a is press-fitted to a hermetically sealed vessel 10 from a direction of a side surface of the fixed scroll 1 (right side in Figure 1) by penetrating the hermetically sealed vessel 10. A rotating scroll 2 has a seat 2a. On one surface of the seat 2a (upper side in Figure 1), a spiral turbine 2b having substantially the same shape as that of the spiral turbine 1b of the fixed scroll 1 is formed, and in a central portion of the reverse side of the spiral turbine 2b of the seat 2a (lower side in Figure 1), a boss 2f having a hollow cylindrical shape is formed. In an inner side surface of the boss 2f, a bearing 2c is formed. In an outer peripheral part on the same side as that of the boss 2f of the rotating scroll, a thrust face 2d, which is slidably in contact with a thrust bearing 3a of a compliant frame, is formed. Further, in an outer periphery of the seat 2a of the rotating scroll 2, a pair of Oldham's coupling grooves 2e are formed substantially in line, with a phase shift of 90° in respect of the Oldham's coupling grooves 1c of the fixed scroll 1. A pair of rotating projections 9a of the Oldham's coupling 9 are engaged with the Oldham's coupling grooves 2e so as to be reciprocally slidable. The seat 2a is formed with an intermediate pressure passage 2j, which is a narrow hole connecting a surface on the side of the fixed scroll 1 (upper surface in Figure 1) to a surface on the side of compliant frame 3 (lower surface in Figure 1). An aperture on the surface on the compliant frame side of the intermediate pressure passage 2j, i.e. a lower entrance, is positioned so that a circular locus thereof is always within an inside of the thrust bearing 3a of the compliant frame 3 in normal operation. The intermediate pressure passage 2j can be a single slant hole as shown in Figure 1 or can be composed of three holes and an intermediate pressure passage 2ℓ (Figure 2) and there is no substantial difference therebetween. In a central portion of the compliant frame 3, a main bearing 3c and an auxiliary main bearing 3h, both for radially supporting a main shaft 4 rotatably driven by a motor 7, are formed. Further, a connection passage 3s connecting from the surface of the thrust bearing 3a to a space 15f is formed on the compliant frame 3. Adjust valve housing is also formed in the compliant frame 3, one end of which adjust valve housing 3p (lower end in Figure 2) is connected to an outer boss space 2h around boss 2f through an adjust valve inlet path 3j and simultaneously the other end of which (upper end in Figure 2) is connected to a space 2i around the outer periphery of seat 2a through an adjusting valve outlet path 3n. In a lower portion of an adjusting valve housing 3p, an intermediate pressure adjusting valve 3ℓ is accommodated so as to be reciprocally slidable. In an upper portion of the adjusting valve housing 3p, a spring stopper 3t is accommodated by fixing it to the compliant frame 3. Between the intermediate pressure adjusting valve 3ℓ and the spring stopper 3t, an intermediate pressure adjusting spring 3m is accommodated by being compressed shorter than the expanded length thereof. Although an outer peripheral surface 15g of the guide frame 15 is fixed to the hermetically sealed vessel 10 by an interference shrink fit or welding, a flow path for introducing a high-pressure refrigerating gas, discharged from a discharge port 1f of the fixed scroll 1, from the guide frame 15 to a discharge tube 10b installed on the motor side (lower side in Figure 1) is maintained. On the fixed scroll side of the guide frame 15 (the upper side in Figure 1), on an inner side surface an upper bore surface 15a is formed and engaged with an upper cylindrical surface 3d formed on an outer peripheral surface of the compliant frame 3. On the other hand, on the motor side of the guide frame 15 (lower side in Figure 1), on the inner side surface a lower bore surface 15b is formed and engaged with a lower cylindrical surface 3e formed on the outer peripheral surface of the compliant frame 3. In an inner side surface of the guide frame 15, two ring-shaped seal grooves for accommodating seals are formed, in which seal grooves, a ring-shaped upper seal 16a and a ring-shaped lower seal 16b are inserted and seated. The above-mentioned space 15f is delimited by these two seals 16a, 16b, the inner side surface of the guide frame 15, and the outer side surface of the compliant frame 3. Each of the upper seal 16a end the lower seal 16b is not necessarily indispensable and can be omitted by sealing a micro-gap between engaged portions, for example, by forming an oil film. A space on the outer peripheral side of the thrust bearing 3a surrounded by the seat 2a of the rotating scroll and the compliant frame in the vertical directions, namely the space 2i, is connected to a suction chamber 1g in the vicinity of the outer end of the spiral turbine, whereby it has a low pressure under an atmosphere of suction gas. At the end on the side of the rotating scroll of the main shaft 4 (upper side in Figure 1), an orbit shaft body 4b rotatably engaged with the bearing 2c of the rotating scroll 2 is formed. Beneath the end, a main shaft balancer 4e is fixed by an interference shrink fit, and a main shaft body 4c rotatably engaged with the main bearing 3c and the auxiliary main bearing 3h, both of the compliant frame 3, is formed. At the other end of the main shaft, a subshaft body 4d rotatably engaged with a subbearing 6a of a subframe 6 is formed. Between the subshaft body 4d and the main shaft body 4c, a rotor 8 of the motor 7 is fixed by an interference shrink fit. To an upper end surface of the rotor 8, an upper balancer 8a is fastened, and to a lower end of the rotor, a lower balancer 8b is fastened, wherein three balancers including the main shaft balancer 4e adjust a static balance and a dynamic balance. Further, an oil pipe 4f is press-fitted into the end surface of the main shaft 4 in order to suck up refrigerating oil 10e accumulated in a bottom portion of the hermetically sealed vessel 10. It is possible to omit the oil pipe 4f by extending the main shaft 4. A glass terminal 10f is attached to a side surface of the hermetically sealed vessel 10, to which glass terminal a lead wire from a stator of the motor 7 is connected. In the next, normal operation of the scroll compressor according to Embodiment 1 will be described. In the normal operation, because a region 10a of the hermetically sealed vessel 10 has a high pressure under an atmosphere of discharge gas, the refrigerating oil 10e in the bottom portion of the hermetically sealed vessel 10 is introduced into a space 2g in the boss 2f through a high pressure lubrication hole 4g, penetrating the oil pipe 4f and the main shaft 4 in the axial direction. This high-pressure oil is depressurized by the bearing 2c so as to be an intermediate pressure higher than a suction pressure and the same as a discharge pressure or less and flows into the space 2h around the boss 2f. On the other hand, a high-pressure oil in the high pressure lubrication hole 4g is introduced into the high pressure end of the main bearing 3c (lower end surface in Figure 1) from a side aperture formed in the main shaft 4, wherein it becomes to have the intermediate pressure by being depressurized by the main bearing 3c and flows into the space 2h. The refrigerating oil having the intermediate pressure of the space 2h, which refrigerating oil is generally in a two phase state including a gas refrigerant and the refrigerating oil by gassing of the refrigerant dissolved in the refrigerating oil, passes through an adjusting valve inlet path 3j; flows into an adjusting valve housing 3p in an atmosphere of the suction pressure i.e. a low pressure by defeating a load applied by an intermediate pressure adjusting spring 3m to push up an intermediate pressure adjusting valve 3ℓ; and is released in the space 2i through an adjust valve outlet path 3n. As described, the intermediate pressure Pm1 of the space 2h is controlled by a predetermined pressure a substantially determined by spring force of the intermediate pressure adjusting spring 3m and the area exposed to the intermediate pressure of the intermediate pressure adjusting valve 3ℓ as follows: Pm1 = Ps + α, where Ps designates a pressure of suction atmosphere, i.e. a low pressure. In Embodiment 1, it is possible to realize stable lubrication to the bearings because of the pressure relationship of: suction area (space 2i) < space 2h around boss 2f < discharge area (area 10d of hermetically sealed vessel); and the refrigerating oil in the atmosphere of high pressure in the discharge area stably flows into the space around the boss by a predetermined pressure difference determined by a pressure adjusting device. Incidentally, an entrance 2k of the intermediate pressure passage 2j installed in the seat 2a of the rotating scroll 2 is constantly or intermittently connected to an opening portion on a thrust bearing side of the connection passage 3s formed in the compliant frame 3, i.e. an entrance 3u (upper opening portion in Figure 2). Therefore, a refrigerant gas having an intermediate pressure higher than a suction pressure in a middle of compressing operation in the compression chamber, which is composed of the fixed scroll 1 and the rotating scroll 2, and the same as a discharge pressure or less is introduced into the space 15f through the intermediate pressure passage 2j of the rotating scroll 2 and the connection passage 3s of the compliant frame 3. However, because the space 15f is a closed area sealed by the upper seal 16a and the lower seal 16b, the compression chamber and the space 15f is in so-called breathing state, in which there are bidirectional minute flows between the compression chamber and the space 15f in response to a pressure variation of the compression chamber in the normal operation. As described, an intermediate pressure Pm2 in the space 15f is controlled by a predetermined magnification β substantially determined by a position of the connecting compression chamber as follows: Pm2 = Ps × β, where Ps designates a pressure of suction atmosphere, i.e. a low pressure. Although the sum of force caused by the intermediate pressure Pm1 in the space 2h around boss 2f and a pressure of pushing from the rotating scroll 2 through the thrust bearing 3a effects a downward force, the sum of force caused by the intermediate pressure Pm2 in the space 15f and force caused by a high pressure acting on a portion exposed to the atmosphere of high pressure on the end surface effects an upward force, wherein the upward force is set to be larger than the downward force in the normal operation. Therefore, the upper cylindrical surface 3d of the compliant frame 3 is guided by the upper bore surface 15a and the lower cylindrical surface 3e of the compliant frame 3 is guided by the lower bore surface 15b. In other words, the compliant frame 3 can slide on the guide frame 15 and floats on the fixed scroll side (upward direction in Figure 1). The rotating scroll 2 pushed up by the compliant frame 3 through the thrust bearing 3a also floats upward. Consequently, tops and bottom of the rotating scroll 2 are slidably in contact with bottom and tops of the fixed scroll 1 respectively. In Embodiment 1, because the space 2h around boss 2f, of which inner pressure is the intermediate pressure higher than a suction pressure, is formed, there is an effect that the rotating scroll 2 is separated from the compliant frame 3 in the axial direction; and contact force between the thrust surface of the rotating scroll 2 and the thrust bearing of the compliant frame 3 is partially reduced, whereby a sliding loss of the rotating scroll can be reduced and seizure of the thrust bearing caused by an excessive load can be avoided. In the next, basic operation in starting up will be described in reference of Figure 2. Generally, before starting up, a pressure in the hermetically sealed vessel 10 is uniform, which pressure is so-called balance pressure. The suction atmosphere and the discharge atmosphere have the same pressure. The pressure of the suction atmosphere decreases along with compressing operation just after starting up, and the pressure of the discharge atmosphere increases along with the compressing operation. In the scroll compressor of frame compliant type according to Embodiment 1, a pressure slightly higher than the balance pressure of just before starting up, i.e. the balance pressure × β, is introduced into the space 15f just after starting up. In the conventional scroll compressor of frame compliant type, an inner pressure in the hermetically sealed vessel 10, namely a pressure of the discharge atmosphere, is increased and thereafter a pressure in the space 15f is increased. However, in Embodiment 1, the pressure in the space 15f increases earlier than a rise of the pressure of the discharge atmosphere. Therefore, the compliant frame 3 is lifted up within a relatively short period and the rotating scroll 2 is lifted up along therewith so as to be slidably in contact with the fixed scroll 1 in the axial direction, whereby the normal operation is ready. Thus a highly efficient compression having an excellent starting-up property is realized. If, in the conventional scroll compressor of frame compliant type, namely a compressor of which space 2h around the boss 2f and space 15f are connected by a pressure equalizing aperture 3i (Fig.8) to make these substantially the same area, an intermediate pressure in the space 2h and an intermediate pressure in the space 15f are generated by introducing a refrigerant gas in course of compression (intermediate pressure = suction pressure × β). Therefore, although it seems that a compressor having an excellent starting-up property is obtainable in a similar manner to those described in Embodiment 1 since the pressure in the space 15f is increased just after starting up, there are the following two problems. The first problem is that since the pressure in the space 2h is increased in synchronism with increment of the pressure in the space 15f, force of separating the rotating scroll 2 from the compliant frame 3 is increased and thereby the rotating scroll becomes unstable. Therefore, a gap causing a leak between the thrust surface 2d of the rotating scroll 2 and the thrust bearing 3a of the compliant frame 3 is increased; the intermediate pressure in the space 15f is decreased to thereby deteriorate the starting-up property; and a danger in terms of reliability by an insufficient contact of the bearings may be caused. The second problem is that a state that the pressure in the space 2h is higher than the pressure of the refrigerating oil 10e accumulated in the bottom portion of the hermetically sealed vessel 10, i.e. the discharge pressure in the hermetically sealed vessel, continues for a certain amount of time after starting up since the pressure in the space 2h increases in synchronism with the pressure increment in the space 15f. Accordingly, lubrication by a pressure difference of the refrigerating oil 10e is not instantaneously started and the bearing 2c and the main bearing 3c are not supplied with the refrigerating oil for this moment even though the scroll compressor is in a running state, whereby troubles in terms of reliability such as wear and seizure of the bearings are caused. On the contrary, in Embodiment 1 of the present invention, a highly efficient compressor having high reliability, in which an improvement in the starting-up property and lubricating just after starting up is assured, is realized. In the scroll compressor of frame compliant type according to Embodiment 1 of the present invention, when the rotating scroll 2 flaps on the thrust bearing 3a of the compliant frame 3 owing to an outer disturbance although the intermediate pressure Pm1 in the space 2h is decreased, the intermediate pressure Pm2 in the space 15f is not decreased, whereby the rotating scroll 2 does not easily relieve. Thus a highly efficient compressor having high reliability is realized. Additionally, the space 2h and the space 15f are not connected each other and are formed as independent areas in terms of pressure. Therefore, a compact compressor at a low cost having a high degree of freedom in setting areas, on which a pressure in the axial directions acts, within various spaces, is realized. In Embodiment 1, an example that the space 2h is made to be the intermediate pressure by adopting the intermediate pressure adjusting spring 3m and the intermediate pressure adjusting valve 3ℓ is described. However, a similar effect is obtainable by adopting a structure that the space 2h is made to be a space having a low pressure (atmosphere of intake) as in the space 2i around outer periphery of seat 2a by directly connecting the space 2h to the space 2i without adopting the intermediate pressure adjusting spring 3m and the intermediate pressure adjusting valve 3ℓ. In the next, the maximum movable distance in the axial direction will be described with reference to Figures 3a through 5. In the normal operation, the compliant frame 3 floats along with the rotating scroll 2 as shown in Figure 3a, wherein there is a gap having the maximum movable distance in the axial direction, i.e. the maximum amount of relieving in the axial direction, exists between the compliant frame 3 and the guide frame 15. On the other hand, because the compliant frame 3 is in contact with the guide frame 15 in the axial direction under the relieved state, there is no gap in the axial direction therebetween as shown in Figure 3b. Figure 4 shows a rise of the inner pressure at a time of compressing a liquid refrigerant. In Figure 4, the abscissa represents the maximum amount of relieving in the axial direction, which is an interval in the axial direction between the compliant frame and the guide frame under the normal operation, and the ordinate represents the maximum pressure generated in the compression chamber at a time of compressing a liquid refrigerant, a refrigerating oil and so on. As shown, when the maximum amount of relieving in the axial direction is 30 µm or less, because the maximum pressure generated in the compression chamber exceeds a permissible pressure, there is a danger that troubles in terms of reliability such as destruction including fatigue failures of the spiral turbine of the fixed scroll and the spiral turbine of the rotating scroll and abnormal wear and seizure caused along with an increment of a load to the bearings. In the scroll compressor of frame compliant type according to Embodiment 1 of the present invention, because the maximum amount of relieving in the axial direction is set to be 30 µm or more, there is no danger of causing the above-mentioned troubles in reliability. Generally, in the scroll compressor of which rotating scroll was independently movable in the axial direction, there was a danger that the shaft is seized by an increment of occasions that the bearing was partially held when the rotating scroll was relieved under a condition that the maximum amount of relieving in the axial direction of the rotating scroll was set to be large. In scroll compressors of frame compliant type not limited to that described in Embodiment 1, a degree that the bearing is partially held is not increased because the rotating scroll and the compliant frame integrally move in the vertical directions at a time of relieving. Figure 5 shows a starting-up property. The abscissa represents the maximum amount of relieving in the axial direction as in Figure 4, and the ordinate represents a time required for starting-up, i.e. a time from starting-up through floating of the compliant frame to the normal operation, specifically the time required for starting-up means a period necessary for transferring from a relieved state to an ordinary running in which a compliant frame and a rotating scroll integrally float and tops and a bottom of the rotating scroll are slidably in contact with a bottom and tops of a fixed scroll respectively. As shown in Figure 5, because the starting-up time exceeds a permissible start-up time when the maximum amount of relieving in the axial direction is 300 µm or more, there is danger that a starting-up property is not sufficient or the starting-up is impossible as a defect in some occasions. Because the maximum amount of relieving in the axial direction is set to be 300 µm or less in the scroll compressor of frame compliant type according to Embodiment 1, there is no danger of causing such troubles in terms of reliability and deficiency. Although a part or all of overturning moment generated in the rotating scroll 2 is transmitted through the thrust bearing 3a to the compliant frame 3, because resultant force of a load received from the main bearing 3c and a reaction to the load, namely coupled force of reaction force received from the guide frame 15 through the upper cylindrical surface 3d and reaction force received from the guide frame 15 through the lower cylindrical surface 3e, effects to cancel the overturning moment, excellent stability in follow-up operation in the normal operation and excellent stability in relieving are obtainable as in the conventional scroll compressor of frame compliant type. EMBODIMENT 2 Embodiment 2 of the present invention will be described in reference of Figure 6. Figure 6 is a longitudinal cross-sectional view of an important part according to Embodiment 2 of the present invention. the other parts are similar to those described in Embodiment 1 and description is omitted. An adjusting valve housing 3p is formed in the compliant frame 3. An end of the adjust valve housing 3p (lower end in Figure 6) is connected to the space 15f through an adjusting valve inlet path 3j, and the other end thereof (upper end in Figure 6) is connected to the space 2i around outer periphery of seat 2a through an adjusting valve outlet path 3n. In a lower part of the adjusting valve housing 3p, an intermediate pressure adjusting valve 3ℓ is slidably accommodated, in an upper portion, a spring stopper 3t is accommodated, which spring stopper is secured to the compliant frame 3. An intermediate pressure adjusting spring 3m is accommodated between the intermediate adjusting valve 3ℓ and the spring stopper 3t by being compressed shorter than the expanded length. Further, a check valve housing 3v is formed in the compliant frame 3, wherein an end of the check valve housing 3v (upper end in Figure 6) is connected to the space 2h through a check valve inlet path 3w, and the other end (lower end in Figure 6) is connected to the space 15f through a check valve outlet path 3x. In an upper portion of the check valve housing 3v, a check valve 3y is slidably accommodated, and in a lower portion, a spring stopper 3z is accommodated, which spring stopper 3z is secured to the compliant frame 3. A check valve spring 3b is accommodated between the check valve 3y and the spring stopper 3z by being compressed shorter than the expanded length. Two ring-shaped seal grooves for accommodating seals are formed in an inner side surface of the guide frame 15, to which seal grooves a ring-shaped upper seal 16a and a ring-shaped lower seal 16b are fitted respectively. The two seals 16a, 16b, an inner side surface of the guide frame 15, and an outer side surface of the compliant frame 3 delimit the space 15f. However, the upper seal 16a and the lower seal 16b are not necessarily indispensable, and these can be omitted by sealing micro-gaps of engaging portions, for example, by forming an oil film. An area on an outer peripheral side of the thrust bearing surrounded by the seat 2a of the rotating scroll and the compliant frame 3 in the vertical directions, i.e. the space 2i, is connected to a suction area in the vicinity of an outer end of the spiral turbine and therefore is in an atmosphere of suction gas. In the next, the normal operation of the scroll compressor according to Embodiment 2 will be described. Because a space 10d of hermetically sealed vessel 10 has a high pressure under an atmosphere of discharge gas in the normal operation, a refrigerating oil in a bottom portion of the hermetically sealed vessel is introduced into a space 2g in the boss 2f through a high pressure lubrication hole 4g formed in the main shaft 4 by penetrating in the axial direction. A high pressure oil is depressurized by a bearing 2c to be an intermediate pressure higher than a suction pressure and the same as a discharge pressure or less, whereby it flows into a space 2h around the boss 2f. On the other hand, as another route, the high pressure oil from the high pressure lubrication hole 4g is introduced into an end face on the high pressure side of a main bearing 3c (lower end in Figure 6) through a side hole formed in the main shaft 4 and depressurized by the main bearing 3c to be the intermediate pressure, whereby the high pressure oil flows into the space 2h around boss 2g. The refrigerating oil, which is generally in a two-phase state of a gas refrigerant and the refrigerating oil by gassing of the refrigerant dissolved in the refrigerating oil, having the intermediate pressure in the space 2h around the boss 2f passed through a check valve inlet path 3w, flows into the check valve housing 3v by defeating force applied by the check valve spring 3b and pushing up the check valve 3y, and thereafter is released in the space 15f having the other intermediate pressure higher than the suction pressure and the same as the discharge pressure or less. Thereafter, the refrigerating oil having the other intermediate pressure in the space 15f, which refrigerating oil is generally in a two-phase state of a gas refrigerant and the refrigerating oil by gassing of the refrigerant dissolved in the refrigerating oil, passes through the adjusting valve inlet path 3j, flows into the adjusting valve housing 3p in an atmosphere of suction pressure, i.e. a low pressure, by defeating force applied by the intermediate pressure adjusting spring 3m and pushing up the intermediate pressure adjusting valve 3ℓ, and is released in the space around outer periphery of seat through the adjusting valve outlet path 3n. As described, the intermediate pressure Pm2 in the space 15f is controlled by a predetermined pressure α1 substantially determined by spring force of the intermediate pressure adjusting spring 3m and the area exposed to the space of the intermediate pressure adjusting valve 3ℓ as follows: Pm2 = Ps + α1, where Ps designates a pressure of suction atmosphere, i.e. a low pressure. Incidentally, the intermediate pressure Pm1 in the space 2h is controlled by a predetermined pressure α2 substantially determined by spring force of the check valve spring 3b and the check valve area exposed to the space 2h as follows: Pm1 = Pm2 + α2 = Ps + (α1 + α2). As described, in the scroll compressor of frame compliant type according to Embodiment 2 of the present invention, because the check valve for allowing a flow of fluid from the space 2h to the space 15f and simultaneously preventing the adverse flow, which is a flow of fluid from the space 15f to the space 2h, is installed, although the intermediate pressure Pm1 in the space 2h is decreased in a case that the rotating scroll 2 flaps on the thrust bearing 3a of the compliant frame 3 owing to an outer disturbance, the intermediate pressure Pm2 in the space 15f is not decreased by such a decrement and therefore the rotating scroll 2 is not easily relieved. Further, a highly efficient compressor having high reliability in which lubrication function is not spoiled, is realized. Because the parameter α2 can be easily and freely adjusted by setting the spring force of the check valve spring 3b, the space 2h and the space 15f can be practically treated as independent areas. Accordingly, a compact compressor at a low cost, in which a degree of freedom in setting areas receiving a pressure in the axial directions within the two areas having the intermediate pressures, is realized. Further, because the bottom portion of the hermetically sealed vessel accumulating the refrigerating oil is made to be a high pressure, of which the magnitude is around that of the discharge pressure; the space 2h is in a middle of the lubrication route; and the space is connected to the area having a low pressure through a pressure adjusting device in Embodiment 2, the pressures always have a relationship of: suction area (space 2i) < space 15f < space 2h < discharge area (space 10d). Therefore, lubrication to the bearings becomes stable because the refrigerating oil in the atmosphere of high pressure in the discharge area stably flows into the space around boss by a predetermined pressure difference determined by the pressure adjusting device and the check valve. In Embodiment 2, the check valve 3y is used as a means for allowing the flow of fluid from the space 2h around the boss 2f to the space 15f and preventing the adverse flow, i.e. the flow of fluid from the space 15f to the space 2h. However, the means is not limited to the check valve and other means can be used as long as a similar effect is obtainable. In the next, operation at a time of starting up will be described in reference of Figure 6. Generally, an inner pressure of the hermetically sealed vessel 10 is uniform just before starting up, which inner pressure is so-called balance pressure. Therefore, the suction atmosphere has the same pressure as that of the discharge atmosphere. Just after starting up, the pressure of the suction atmosphere decreases along with compressing operation, and the pressure in the discharge atmosphere increases along with the compressing operation. In the scroll compressor of frame compliant type according to Embodiment 2, the intermediate pressure Pm1 in the space 2h decreases by following a drop of the pressure in the suction atmosphere, and an accompanying pressure decreases in the space 2i around the outer periphery of the seat 2a just after starting up. On the other hand, the pressure in the discharge atmosphere increases just after starting up, wherein the pressure difference for supplying the refrigerating oil accumulated in the bottom portion of the hermetically sealed vessel 10 to the bearing 2c and the main bearing 3c is obtainable just after starting up. Thus, a compressor having high reliability, in which lubrication to the bearings is sufficiently assured, even in timing of just after starting up, is obtainable. As described, two sets of a valve and a spring module are respectively installed between the space 2h and the space 15f for generating the pressure difference of α2 and between the space 15f and the area of low pressure atmosphere for generating the pressure difference of α1, and the compressor is controlled by the formulas of Pm1 = Ps + (α1 + α2) and Pm2 = Ps + α1. However, a similar effect is obtainable as another method by respectively installing two sets of a valve and a spring module between the space 2h and the space of low pressure atmosphere for generating the pressure difference of α2 and between the space 15f and the space of low pressure atmosphere for generating the pressure difference of α1 and also by controlling the compressor in accordance with formulas of Pm1 = Ps + α2 and Pm2 = Ps + α1. In this case, a simple structure that a refrigerating oil depressurized by the bearing 2c to be an intermediate pressure is introduced into the space 2h and a refrigerating oil depressurized by the main bearing 3c to be an intermediate pressure is introduced into the space 2h is obtainable. EMBODIMENT 3 Embodiment 3 of the present invention will be described with reference to Figure 7. Figure 7 is a longitudinal cross-sectional view of an important part of Embodiment 3 of the present invention. The other parts are similar to those described in Embodiment 1 and description is omitted. In the seat 2a of the rotating scroll 2, an intermediate pressure passage for connecting a surface on the fixed scroll side (upper surface in Figure 7) to a surface on the side of compliant frame 3 (lower surface in Figure 7), which is a narrow aperture, is formed. An opening portion on the surface on the compliant frame side of the intermediate pressure passage 2j, i.e. a lower entrance 2k, is positioned so that a circular locus thereof is always included in the thrust bearing 3a of the compliant frame 3 in the normal operation. Further, a second intermediate pressure passage 2m which is another narrow hole for connecting the surface on the fixed scroll side (upper surface in Figure 7) to the surface on the compliant frame side (lower surface in Figure 7) is formed in the seat 2a. An opening portion of second intermediate pressure passage 2m on the compliant frame side is positioned so that a circular locus thereof is constantly or intermittently connected to the space 2h in the normal operation. Further, a connection passage 3s for connecting the surface of the thrust bearing 3a to the space 15f is formed in the compliant frame 3. Two seal ring-shaped grooves for accommodating seals are formed in an inner side surface of the guide frame 15, to which seal grooves a ring-shaped upper seal 16a and a ring-shaped lower seal 16b are fitted. These two seals 16a, 16b, the inner side surface of the guide frame 15, and an outer side surface of the compliant frame 3 delimit the space 15f. However, the upper seal 16a and the lower seal 16b are not necessarily indispensable and can be omitted by sealing a micro-gap in engaging portions, for example, by forming an oil film. An area on an outside of an outer periphery of the thrust bearing 3a, which is surrounded by the seat 2a of the rotating scroll and the compliant frame 3 in the vertical directions, namely the space 2i, is in an atmosphere of suction gas because it is connected to a suction area in the vicinity of an outer end of the spiral turbine. In the next, operation of the scroll compressor according to Embodiment 3 in the normal operation will be described. Because the space 10d of hermetically sealed vessel 10 has a high pressure of an atmosphere of discharge gas in the normal operation, a refrigerating oil in a bottom portion of the hermetically sealed vessel is introduced into the space 2h through a high pressure lubrication hole 4g formed in the main shaft 4 by penetrating in the axial direction. A high pressure oil is depressurized by a bearing 2c to be an intermediate pressure and flows into the space 2h. On the other hand, as another route, the high pressure oil from the high pressure lubrication hole 4g is introduced into an end surface on the high pressure side of a main bearing 3c (lower end in Figure 7) through a side hole formed in the main shaft 4, is depressurized by the main bearing 3c to be an intermediate pressure, and similarly flows into the space 2h. The refrigerating oil having the intermediate pressure in the space 2h, which is generally in a two phase state of a gas refrigerant and the refrigerating oil by gassing of the refrigerant dissolved in the refrigerating oil, flows into the compression chamber formed by the fixed scroll 1 and the rotating scroll 2 through the second intermediate pressure passage 2m. In other words, the refrigerating oil is injected into a refrigerant gas in a middle of compressing operation. As described, the intermediate pressure Pm1 in the space 2h is controlled by a predetermined magnification β1 substantially determined by a position of the compression chamber substantially connected to the second intermediate pressure passage 2m, the amount of the refrigerating oil to be injected and so on as follows: Pm1 = Ps × β1, where Ps designates a pressure of suction atmosphere, i.e. a low pressure. On the other hand, the entrance 2k of the intermediate pressure passage 2j formed in the seat 2a of the rotating scroll 2 is constantly or intermittently connected to an opening portion on the thrust bearing side of the connection passage 3s formed in the compliant frame 3, i.e. an entrance 3u (an upper opening portion in Figure 7). Therefore, the refrigerant gas in a middle of compressing operation from the compression chamber formed by the fixed scroll 1 and the rotating scroll 2 is introduced into the space 15f through the intermediate pressure passage 2j in the rotating scroll 2 and the connection passage 3s in the compliant frame 3. However, because the space 15f is a closed area sealed by the upper seal 16a and the lower seal 16b, there is a minute bidirectional flows between the compression chamber and the space 15f in response to a pressure variation in the compression chamber in the normal operation as if breathing. As described, the intermediate pressure Pm2 in the space 15f is controlled by a predetermined magnification β2 substantially determined by a position of the compression chamber substantially connected to the intermediate pressure passage 2j as follows: Pm2 = Ps × β2, where Ps designates a pressure of suction atmosphere, i.e. a low pressure. As described, in the scroll compressor of frame compliant type according to Embodiment 3 of the present invention, because the space 2h and the space 15f are independently formed by separate areas, when the rotating scroll 2 flaps on the thrust bearing 3a of the compliant frame 3 owing to an outer disturbance, although the intermediate pressure Pm1 in the space 2h is decreased, the intermediate pressure Pm2 in the space 15f is not decreased by such a decrement, whereby the rotating scroll is not easily relieved. Thus a highly efficient compressor having high reliability is realized. In the next, operation in starting up will be described in reference of Figure 7. Generally, an inner pressure of the hermetically sealed vessel 10 is uniform just before starting up, which pressure is so-called balance pressure. In other words, a suction atmosphere and a discharge atmosphere have the same pressure. Just after starting up, a pressure in the suction atmosphere decreases along with compressing operation, and a pressure in the discharge atmosphere increases along with the compressing operation. In the scroll compressor of frame compliant type according to Embodiment 3, a pressure a slightly higher than the balance pressure of just before starting up, i.e. balance pressure × β2, is introduced into the space 15f just after starting up. Accordingly, a pressure in the space 15f increases earlier than the pressure in the discharge atmosphere, whereby the compliant frame 3 is lifted up within a relatively short period and simultaneously the rotating scroll 2 is lifted up so as to be slidably in contact with the fixed scroll 1 in the axial direction, whereby a state of the normal operation is prepared. Thus a highly efficient compressor having an excellent starting-up property is realized. Additionally, because the space 2h and the space 15f are formed as independent areas, a compact compressor at a low cost, which has a high degree of freedom in setting areas receiving a pressure in the axial directions within the respective areas having the intermediate pressures, is realized. In Embodiments 1 to 3, a hermetic compressor mainly used in small size and medium size refrigerating machines and air conditioners is exemplified. However, similar effects are obtainable in a compressor having operating elements in an outside of a container accommodating compressing elements, which compressor is mainly used for air conditioners for automobile. Further, in Embodiments 1 to 3, a scroll compressor of a high-pressure shell type, of which space of hermetically sealed vessel 10d has an atmosphere of discharge gas or a high pressure of which magnitude is around that of the atmosphere of discharge gas, is exemplified for the description. However, substantially similar functions and effects are obtainable by using a scroll compressor of a low-pressure shell type, of which space 10d of hermetically sealed vessel 10 has an atmosphere of suction gas or a low pressure of which the magnitude is around that of the atmosphere of suction gas, by installing an oil pump in an end of a main shaft 4, and by supplying a refrigerating oil 10e by a pressure of the pump. The first advantage of a scroll compressor according to the present invention is that a pressure higher than a suction pressure in a space and the same as a discharge pressure or less is not decreased, even though a rotating scroll flaps by a tiny outer disturbance such as variations of a pressure condition for operating and suction of a liquid refrigerant and therefore the rotating scroll is not easily relieved, whereby a highly efficient compressor having high reliability is obtainable. The second advantage of a scroll compressor according to the present invention is that a rotating scroll is separated from a compliant frame in an axial direction because a space around boss has a higher pressure than a suction pressure; contact force between a thrust surface of the rotating scroll and a thrust bearing of the compliant frame is partially reduced; and a sliding loss of the rotating scroll is reduced and seizure of the thrust bearing caused by an excessive load is avoidable, whereby a highly efficient compressor having high reliability is obtainable. The third advantage of a scroll compressor according to the present invention is that a rotating scroll is not easily relieved because a pressure in a space is not decreased by preventing a counter flow of fluid in spite of a decrement of an intermediate pressure in a space around boss caused when the rotating scroll flaps by a tiny outer disturbance such as variations in a pressure condition for operation and suction of a liquid refrigerant; and introduction of a pressure into the space becomes easy, whereby a compressor having high reliability at a low cost is obtainable. The fourth advantage of a scroll compressor according to the present invention is that lubrication to bearings becomes stable because a refrigerating oil in an atmosphere of high pressure stably flows into a space around boss by a predetermined pressure difference determined by a pressure adjusting device or the like under a constant relationship of: pressure in suction area < pressure in space < pressure in space around boss < pressure in discharge area; and therefore a friction coefficient of bearings can be made small and seizure of the bearings is avoidable, whereby a highly efficient compressor having high reliability is obtainable. The fifth advantage of a scroll compressor according to the present invention is that a working area of a space is not restricted by a working area of a space around boss, namely a degree of freedom in setting the working areas becomes high because a pressure in the space around boss and a pressure in the space are separately set, whereby a compact compressor having high reliability and high efficiency is obtainable. The sixth advantage of a scroll compressor according to the present invention is that lubrication to bearing becomes stable because a refrigerating oil in a atmosphere of high pressure in a discharge area stably flows into a space around boss by a predetermined pressure difference determined by a pressure adjusting device under a constant relationship of: pressure in suction area < pressure in space around boss < pressure in discharge area; and therefore a friction coefficient of bearings becomes small and seizure of the bearings is avoidable, whereby a highly efficient compressor having high reliability is obtainable. The seventh advantage of a scroll compressor according to the present invention is that a starting-up property is excellent because normal operation is attained by a rise of a pressure in a space, which pressure is a major factor for lifting up a compliant frame on a side of fixed scroll just after starting up in response to an increment of a pressure in a compression chamber to thereby making the compliant frame float within a relatively short period, whereby a highly efficient compressor having high reliability is obtainable. The eighth advantage of a scroll compressor according to the present invention is that destruction of scroll turbines and so on caused by an abnormal pressure rise in a compression chamber and seizure of bearings and a main bearing caused by an application of an excessive load are avoidable because a compliant frame is relieved in an axial direction by a relatively large distance before an inner pressure of a compression chamber is abnormally increased; and a starting-up property is excellent by preventing a time for realizing normal operation from extremely lapsing as a result of so-called arbitrary operation without compressing operation when a compliant frame is maximally relieved in an axial direction, namely a rotating scroll is maximally apart from a fixed scroll, at a time of starting because the maximum amount of moving in the axial direction is 300 µm or less, whereby a highly efficient compressor having high reliability is obtainable. Obviously, numerous modifications and variations of the present invention are possible in light of the above teachings. It is therefore to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specifically described herein.

Claims: A scroll compressor comprising: a fixed scroll(1) and a rotating scroll (2) located in a hermetically sealed vessel(10) and respectively having spiral turbines(1B, 2b), wherein the spiral turbines engage each other to form a compression chamber(21) between them; a compliant frame(3) for supporting the rotating scroll (2) in its axial direction and supporting a main shaft(4) for driving the rotating scroll (2) in directions of its radiuses, the compliant frame (3) being movable in the axial direction; and a guide frame(15) for supporting the compliant frame (3) in the directions of the radiuses, in which the rotating scroll (2) is moved in the axial direction along with movement of the compliant frame (3) with respect to the guide frame (15) in the axial direction; characterised in that a frame space (15f) is formed between the compliant frame (3) and the guide frame (15), wherein pressure in the frame space (15f) is higher than suction gas pressure and is the same as discharge gas pressure or less. The scroll compressor according to Claim 1, wherein: the rotating scroll (2) has a thrust face(2d) on a surface opposite to the spiral turbine(2b); the compliant frame (3) has a thrust bearing(3a), sliding on the thrust face (2d) under contacting pressure; and an outer boss space(2h), located inside the thrust bearing (3a) and formed between the compliant frame (3) and the rotating scroll (2), has a pressure higher than the suction gas pressure and the same as the discharge gas pressure or less. The scroll compressor according to Claim 2, wherein the frame space(15f) and the outer boss space(2h) are not directly connected, to make pressures in the frame space (15f) and the outer boss space (2h) independent of each other. The scroll compressor according to Claim 3, wherein: a bottom portion of the hermetically sealed vessel(10), accumulating a refrigerating oil (10e) has a high pressure, whose magnitude is around that of the discharge gas pressure; and the outer boss space(2h) is located in a middle of an oil supplying route and connected to an area (2i) having a low pressure, being an atmosphere of the suction gas pressure, through a pressure adjusting device(23). The scroll compressor according to Claim 2, wherein: the outer boss space (2h) is connected to the frame space (15f); and fluid is allowed to flow only from the outer boss space (2h) to the frame space (15f). The scroll compressor according to Claim 5, wherein pressure(Pm1) in the outer boss space (2h) is higher than pressure(Pm2) in the frame space (15f). The scroll compressor according to Claim 5 or 6, wherein: a bottom portion of the hermetically sealed vessel(10), accumulating a refrigerating oil (10e) has a high pressure, whose magnitude is around that of the discharge gas pressure; the outer boss space(2h) is located in a middle of an oil supplying route; and the frame space(15f) is connected to an area (2i) having a low pressure, being an atmosphere of the suction gas pressure, through a pressure adjusting device(22). The scroll compressor according to any one of Claims 1 to 4, wherein the frame space (15f) is connected to the compression chamber(21) to make pressure in the frame space (15f) higher than the suction gas pressure and the same as the discharge gas pressure or less. The scroll compressor according to Claim3, wherein: the frame space(15f) is connected to the compression chamber(21), and the outer boss space(2h) is connected to the compression chamber (21) independently of the connection between the frame space (15f) and the compression chamber (21). The scroll compressor according to any one of claims 1 to 9, wherein a maximal movable distance of the compliant frame (3) with respect to the guide frame (15) in the axial direction is 30 µm or more and 300 µm or less. The scroll compressor according to Claim 1, wherein: an inside of the hermetically sealed vessel(10) is in an atmosphere of discharge gas; a boss portion(2f) is located on a side opposite to the spiral turbine(2b) in the rotating scroll (2); and an inner boss space(2g) is formed on an inner peripheral side and between the boss portion(2f) and an upper end of the main shaft (4), pressure in the inner boss space (2g) is substantially the same as the discharge gas pressure. The scroll compressor according to Claim 11, wherein: the rotating scroll (2) has a thrust surface(2d) on a side opposite to the spiral turbine(2b); the compliant frame (3) has a thrust bearing(3a), sliding on the thrust surface (2d) under contacting pressure; and an outer boss space(2h), located inside the thrust bearing (3a) and outside the boss portion(2f) and formed between the compliant frame (3) and the rotating scroll (2) has an intermediate pressure higher than the suction gas pressure and lower than the discharge gas pressure. The scroll compressor according to Claim 12, wherein a space (2i) around an outer periphery of a seat(2a) of the rotating scroll (2), positioned further outside the outer boss space(2h) and outside thethrust bearing, has the suction gas pressure. The scroll compressor according to Claim 1, wherein : an inside of the hermetically sealed vessel(10) is in an atmosphere of discharge gas; the rotating scroll has a thrust face(2d) on a surface opposite to the spiral turbine (2b); the compliant frame (3) has a thrust bearing(3a), sliding on the thrust face (2d) under contacting pressure; the rotating scroll(2) has a boss portion(2f), located on a side opposite to the spiral turbine(2b); an outer boss space(2h), located inside the thrust bearing (3a) and outside the boss portion (2f) and formed between the compliant frame (3) and the rotating scroll (2), has a pressure higher than the suction gas pressure and the same as the discharge gas pressure or less; a space(2i) around an outer periphery of a seat (2a) of the rotating scroll (2), positioned further outside the outer boss space(2h) and outside the thrust bearing (3a), has the suction gas pressure; and one pair of projections(9a) of an Oldham's ring(9), restricting autorotation of the rotating scroll (2), are engaged with the rotating scroll, and the other pair of projections(9c) are engaged with the fixed scroll(1). The scroll compressor according to Claim 1, wherein: the rotating scroll (2) has a thrust surface(2d) on a side opposite to the spiral turbine(2b); the compliant frame has a thrust bearing(3a), sliding on the thrust surface (2d) under contacting pressure; an outer boss space(2h) is formed inside the thrust bearing (3a) and between the compliant frame (3) and the rotating scroll (2); an inside of the hermetically sealed vessel (10) has an atmosphere of discharge gas pressure ; and an oil supplying route (3j, 3n) is formed for supplying a lubricating oil, accumulated in a bottom portion of the hermetically sealed vessel (10), from the outer boss space(2h) to a low pressure area (2l) by a pressure difference. The scroll compressor according to Claim 1, wherein: an inside of the hermetically sealed vessel (10) is in an atmosphere of the discharge gas pressure; and the frame space (15f) is delimited by an outer peripheral surface of the compliant frame(3), an inner peripheral surface of the guide flame(15), a lower seal (16b) for preventing intrusion of the discharge gas pressure into the frame space (15f), and a upper seal (16a) for preventing leakage of pressure from the frame space (15f) to a low pressure area of an atmosphere of the suction gas pressure. The scroll compressor according to Claim 1, wherein: an inside of the hermetically sealed vessel (10) is an atmosphere of the discharge gas pressure; the rotating scroll (2) has a thrust face (2d) on a surface opposite to the spiral turbine (2b); a thrust bearing (3a) is formed on the compliant frame (3) so as to slide on the thrust face (2d) under contacting pressure; and an outer boss space (2h), located inside the thrust bearing (3a) and formed between the compliant frame (3) and the rotating scroll (2), has a pressure substantially the same as the suction gas pressure.

Inventors: FUSHIKI TAKESHI, IKEDA KIYOHARU, ISHII MINORU, KAWAGUCHI SUSUMU, OGAWA HIROSHI, OGAWA YOSHIHIDE, SEBATA TAKASHI, SUZUKI YASUHIRO, WATARU IZUMISAWA, FUSHIKI, TAKESHI, IKEDA, KIYOHARU, ISHII, MINORU, KAWAGUCHI, SUSUMU, OGAWA, HIROSHI, OGAWA, YOSHIHIDE, SEBATA, TAKASHI, SUZUKI, YASUHIRO, WATARU, IZUMISAWA
Applicants: MITSUBISHI ELECTRIC CORP, MITSUBISHI DENKI KABUSHIKI KAISHA
Application year: 1999
Main classification: F04C27
IPC codes: F04C23, F04C27, F04C18