JP2002138975A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the airtightness between scrolls, to increase a compression ratio, and to improve a performance of a scroll compressor. SOLUTION: This scroll compressor is provided with a fixed scroll 12 having a volute wall body 12b and a turning scroll 13 having a volute wall body 13b and revoluting by engaging the wall bodies 12b, 13b mutually. The wall bodies 12b, 13b have stepped shapes, and one side faces of end plates 12a, 13a have stepped shapes in which bottom faces 12f, 13f are high and 12g, 13g are low. A chip seal 27d and a chip seal 28d are arranged in a groove 121 and a groove 131, respectively, communicating passages 30, 31 communicating a compression chamber C partitioned by using bottom faces 12f, 13f as a part and having a high pressure with the grooves 121, 131 are formed, respectively, and an internal pressure of the compression chamber C having a high pressure is used as a pressing force of the chip seals 27d, 28d.

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor provided in an air conditioner, a refrigeration system, and the like. 2. Description of the Related Art In a scroll compressor, a fixed scroll and an orbiting scroll are arranged by combining spiral wall bodies, and the orbiting scroll is revolved and orbited with respect to the fixed scroll to form between the wall bodies. The compression of the fluid in the compression chamber is performed by gradually reducing the volume of the compression chamber. The design compression ratio of a scroll compressor is as follows:
The ratio of the maximum volume of the compression chamber (the volume at the time when the compression chamber is formed by the engagement of the walls) to the minimum volume of the compression chamber (the volume immediately before the compression chamber disappears due to the disengagement of the walls). And is represented by the following equation (I). Vi = {A (θsuc) · L} / {A (θtop) · L} = A (θsuc) / A (θtop) (I) In the equation (I), A (θ) is the turning angle θ of the orbiting scroll. A function representing the cross-sectional area parallel to the revolving surface of the compression chamber, the volume of which varies according to the following equation: θsuc is the revolving angle of the revolving scroll when the compression chamber has the maximum volume, and θtop is the revolving angle when the compression chamber has the minimum volume. The turning angle L of the scroll is the wrap (overlap) length between the wall bodies. Conventionally, in order to improve the compression ratio Vi of a scroll compressor, a technique has been adopted in which the number of turns of the wall of both scrolls is increased to increase the cross-sectional area A (θ) of the compression chamber at the maximum capacity. Have been. However, the conventional method of increasing the number of windings on the wall enlarges the outer shape of the scroll and increases the size of the compressor itself, so that it is difficult to adopt the method in an air conditioner for an automobile or the like whose size is severely restricted. was there. In order to solve the above problems, Japanese Patent Publication No. Sho 60-17
In No. 956, both the fixed scroll and the orbiting scroll have a spiral upper edge of the wall with a stepped shape with a lower center side and a higher outer edge, and in response to this stepped shape of the upper edge,
A scroll compressor has been proposed in which both scrolls have a stepped shape in which the side surfaces of the end plates are higher on the center side and lower on the outer peripheral end side. In the above scroll compressor, if the wrap length of the compression chamber at the maximum volume is Ll and the wrap length of the compression chamber at the minimum volume is Ls, the designed compression ratio Vi 'is expressed by the following equation (II). Is done. Vi ′ = {A (θsuc) · Ll} / {A (θtop) · Ls} (II) In the equation (II), the wrap length Ll of the compression chamber at the maximum volume
Is larger than the wrap length Ls of the compression chamber at the time of the minimum volume, and L
Since 1 / Ls> 1, it is possible to improve the designed compression ratio without increasing the number of turns of the wall. [0007] In a conventional general scroll compressor, a tip seal is provided along a spiral upper edge of a wall body, and airtightness between the scroll seal and a bottom surface of the scroll is opposed. The compression efficiency is enhanced by defining a compression chamber with less leakage by securing the compression chamber. In a scroll compressor employing a stepped shape for a scroll as described above, a tip seal is divided and provided at the upper edge of a stepped wall. With respect to the tip seal located on the side, since the pressure introduced to the back surface is small, a sufficient pressing force cannot be obtained against the upper edge of the opposing wall, and the function as a seal cannot be sufficiently exhibited. If the leakage from the compression chamber is large, power for recompression is required by that much, resulting in power loss of the driving source, which is not efficient. The present invention has been made in view of the above circumstances, and in a scroll compressor adopting a stepped shape for a scroll, the function as a tip seal seal is enhanced to suppress leakage from a compression chamber and to prevent leakage. The aim is to increase the operating efficiency by eliminating the power loss spent as recompression power for minutes. [0010] As means for solving the above-mentioned problems, a scroll compressor having the following configuration is employed. That is, a scroll compressor according to claim 1 of the present invention has a spiral scroll body standing upright on one side surface of an end plate, and a fixed scroll fixed at a fixed position and one side surface of the end plate. A orbiting scroll which is supported to be capable of revolving orbiting while being prevented from rotating by engaging the respective wall bodies with each other, and an upper edge of each of the wall bodies, Divided into a plurality of portions and the portion has a stepped shape in which the height of the portion is lower on the center side in the vortex direction and higher on the outer peripheral end side, and one side surface of each end plate also corresponds to each of the portions, In a scroll compressor having a stepped shape having a plurality of portions whose height is higher at a center side in a vortex direction and lower at an outer peripheral end, one or both of the fixed scroll and the orbiting scroll may be provided with each of the wall bodies. Before being located on the outer peripheral end side of the upper edge A seal member disposed along a portion, and the internal pressure of a compression chamber defined by the portion located on the center side of one side surface of each of the end plates or a space communicating with the compression chamber, An introduction path is provided between the portion located on the outer peripheral end side of the upper edge of the wall and the seal member. In this scroll compressor, the center of the compression chamber or the compression chamber is located between the sealing member (tip seal) and the portion of the upper edge of each wall located on the outer peripheral end side through the introduction path. The internal pressure of the space communicating with the compression chamber (for example, the discharge chamber, an oil chamber separated by an oil separator on the discharge side) is introduced, but the internal pressure is much larger than that of the compression chamber located on the outer peripheral end side. ,
Under the pressure, the pressing force of the seal member is also increased,
The function as a seal will be fully exhibited. The fluid introduced to transmit the internal pressure can be either a refrigerant or a refrigerating machine oil. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of a scroll compressor according to the present invention will be described with reference to FIGS. FIG. 1 is a sectional view showing the overall configuration of a scroll compressor according to the present invention. In the figure, reference numeral 11 denotes a housing, which is composed of a housing main body 11a formed in a cup shape and a lid plate 11b fixed to the opening end side of the housing main body 11a. A scroll compression mechanism including a fixed scroll 12 and an orbiting scroll 13 is provided inside the housing 11. The fixed scroll 12 has a configuration in which a spiral wall 12b is erected on one side surface of an end plate 12a. Like the fixed scroll 12, the orbiting scroll 13 has a configuration in which a spiral wall 13b is provided upright on one side surface of the end plate 13a.
Has the same shape as the wall body 12b on the fixed scroll 12 side. A tip seal 2 for improving the airtightness of a compression chamber C, which will be described later, is provided on the upper edges of the walls 12b and 13b.
7 and 28 (these chip seals 27 and 28 are provided).
28 will be described later). The fixed scroll 12 is fastened to the housing body 11a by bolts 14. The orbiting scroll 13 is assembled such that the walls 12b and 13b are engaged with each other in a state where the orbiting scrolls 13 are eccentric with respect to the fixed scroll 12 by the orbital revolving radius and are shifted in phase by 180 °. 13a, and is supported so as to be able to revolve and revolve while being prevented from rotating by a rotation preventing mechanism 15 provided therebetween. A rotary shaft 16 having a crank 16a penetrates the cover plate 11b, and is rotatably supported by the cover plate 11b via bearings 17a and 17b. A boss 18 is provided at the center of the other end surface of the end plate 13a on the orbiting scroll 13 side. Boss 18
The eccentric portion 16b of the crank 16a is rotatably accommodated via a bearing 19 and a drive bush 20, and the orbiting scroll 13 is revolved orbiting by rotating the rotating shaft 16. Rotary axis 1
6 is provided with a balance weight 21 for canceling an unbalance amount given to the orbiting scroll 13. Further, inside the housing 11, a suction chamber 22 is formed around the fixed scroll 12, and a discharge cavity 23 is formed by being divided into an inner bottom surface of the housing body 11a and another side surface of the end plate 12a. ing. The housing body 11a includes a suction chamber 22.
A suction port 24 for guiding a low-pressure fluid toward
At the center of the end plate 12a on the fixed scroll 12 side, a discharge port 25 for guiding a high-pressure fluid from the compression chamber C, which has moved to the center while gradually decreasing the volume, toward the discharge cavity 23 is provided. In the center of the other side surface of the end plate 12a,
A discharge valve 26 that opens the discharge port 25 only when a pressure equal to or greater than a predetermined value acts is provided. FIG. 2 is a perspective view of each of the fixed scroll 12 and the orbiting scroll 13. Fixed scroll 12
The side wall 12b has a spiral upper edge divided into two parts, and has a stepped shape that is lower at the center of the spiral and higher at the outer peripheral end. The wall 13b on the orbiting scroll 13 side
Similarly to the wall 12b, the spiral upper edge is divided into two parts, and has a stepped shape that is lower at the center in the spiral direction and higher at the outer peripheral end. Further, the end plate 12 on the fixed scroll 12 side
“a” has a stepped shape corresponding to each part of the upper edge of the wall 13b, and has two parts where the height of one side surface is higher at the center of the vortex and lower at the outer peripheral end. Similarly to the end plate 12a, the end plate 13a on the orbiting scroll 13 side has a stepped shape having two portions in which the height of one side surface is higher at the center in the vortex direction and lower at the outer peripheral end. The upper edge of the wall 12b is divided into two parts, a lower upper edge 12c provided near the center and a higher upper edge 12d provided near the outer peripheral end.
Between c and 12d, there is a connecting edge 12e that connects the two and is perpendicular to the turning surface. The upper edge of the wall 13b is also
Similarly to b, it is divided into two parts, a lower upper edge 13c provided near the center and a higher upper edge 13d provided near the outer peripheral end. The two parts are connected between the adjacent upper edges 13c and 13d. And a connecting edge 13e perpendicular to the turning surface. The bottom surface of the end plate 12a is divided into two parts, a shallow bottom surface 12f provided near the center and a deep bottom surface 12g provided near the outer peripheral end, and adjacent bottom surfaces 12f and 12g. Between them, there is a connecting wall surface 12h that connects the two and stands vertically. Similarly to the end plate 12a, the bottom surface of the end plate 13a has a shallow bottom surface 13f provided near the center and a deep bottom surface 13 provided near the outer peripheral end.
g is divided into two parts and the adjacent bottom faces 13f, 13
Between g, connecting wall 13h which connects both and stands up vertically
And exists. When the wall 12b is viewed from the direction of the orbiting scroll 13, the connecting edge 12e has a semicircle having a diameter which is smoothly continuous with the inner and outer sides of the wall 12b and has a diameter equal to the wall thickness of the wall 12b. The connecting edge 13e also smoothly continues to the inner and outer side surfaces of the wall 13b similarly to the connecting edge 12e.
It has a semicircular shape with a diameter equal to the wall thickness of 3b. When the end plate 12a is viewed from the direction of the turning axis, the connecting wall surface 12h forms an arc that matches the envelope drawn by the connecting edge 13e with the turning of the turning scroll.
The connecting wall 13h is connected to the connecting edge 12 similarly to the connecting wall 12h.
It forms an arc that matches the envelope drawn by e. In a portion where the upper edge 12d and the connecting edge 12e abut on the wall 12b, as shown in FIG.
2i are provided. The rib 12i is formed integrally with the wall 12b by forming a concave curved surface that is smoothly continuous with the upper edge 12c and the connection edge 12e to avoid stress concentration. A rib 13i having the same shape is provided at a portion where the upper edge 13c and the connection edge 13e abut on the wall 13b for the same reason. The end plate 12a is also provided with a rib 12j at the portion where the bottom surface 12g and the connecting wall surface 12h abut each other. The rib 12j is formed integrally with the wall 12b by forming a concave curved surface that is smoothly continuous with the bottom surface 12g and the connecting wall surface 12h in order to avoid stress concentration. A rib 13j of the same shape is also provided at a portion where the bottom surface 13g and the connecting wall surface 13h abut on the end plate 13a for the same reason.
Is provided. The upper edges 12c, 12e of the wall 12b
And the upper edge 13 in the wall 13b.
The portions where c and 13e meet are ribs 13 at the time of assembly.
j and 12j are chamfered to avoid interference. Further, each upper edge 12c, 1 of the wall 12b
The tip seals 27c and 27d are provided on the connecting edge 12e.
Is provided with a chip seal (seal member) 27e. Similarly, each upper edge 13c, 1 of the wall portion 13
3d is provided with tip seals 28c and 28d,
Is provided with a chip seal (seal member) 28e. Each of the tip seals 27c and 27d has a spiral shape, and is fitted into grooves 12k and 12l formed along the spiral direction on the upper edges 12c and 12d. When the compressor is operating, the grooves 12k and 12l are formed. Is back-pressured by the high-pressure fluid introduced into the bottom surface, and is pressed against the bottom surfaces 13f and 13g to exhibit a function as a seal. The tip seals 28c and 28d also have a spiral shape, and are fitted in grooves 13k and 13l formed along the spiral direction on the upper edges 13c and 13d, and are introduced into the grooves 13k and 13l during operation of the compressor. The back pressure is received by the applied high-pressure fluid, and is pressed against the bottom surfaces 12f and 12g to exhibit a function as a seal. The tip seal 27e has a rod shape, and has a structure in which the tip seal 27e is fitted into a groove 12m formed along the connecting edge 12e and prevents the tip seal 27e from being detached from the groove 12m. As described above, the pressing member (not shown) is pressed against the connecting wall surface 13h to exhibit a function as a seal. The tip seal 28e is also fitted with a groove 13m formed along the connecting edge 13e as in the case of the tip seal 27e, and has a structure for preventing detachment from the groove 13m, and is not shown during operation of the compressor. It is pressed against the connecting wall surface 12h by the urging means to exert a function as a seal. The orbiting scroll 1 is attached to the fixed scroll 12.
3, the lower upper edge 13d has a shallow bottom 1
2f, and the upper edge 13e of the higher position has a deep bottom surface 12g.
Abut. At the same time, the lower upper edge 12d is in contact with the shallow bottom surface 13f, and the higher upper edge 12e is in the deep bottom surface 13f.
abut on g. Thereby, the compression chamber C is formed by being divided into the end plates 12a and 13a and the wall bodies 12b and 13b facing each other between the scrolls (see FIGS. 5 to 8). The compression chamber C moves from the outer peripheral end toward the center with the revolving orbiting movement of the orbiting scroll 13, but the connecting edge 12e is connected to the contacting edge of the walls 12b, 13b.
During the period closer to the outer peripheral end than e, the adjacent compression chambers C (one of which is not in a closed state) slidably contact the connecting wall surface 13h so as not to leak fluid between the adjacent compression chambers C (one is not in a closed state).
As long as the contact points of b and 13b are not closer to the outer peripheral end than the connection edge 12e, the connection wall surface 13h for equalizing pressure between the adjacent compression chambers C (both in a closed state) with the wall body 12 interposed therebetween.
Is not slid on. Similarly, the connection edge 13e is similarly formed on the wall 12b, 1
While the contact point of 3b is located closer to the outer peripheral end than the connection edge 13e, the connection wall surface 12h prevents leakage of fluid between the adjacent compression chambers C (one is not in a closed state) with the wall body 13 interposed therebetween. While the contact points of the wall bodies 12b and 13b are not closer to the outer peripheral end than the connection edge 13e, the pressure is equalized between the adjacent compression chambers C (both in a closed state) with the wall body 13 interposed therebetween. In order to avoid sliding contact with the connecting wall surface 12h. The sliding contact between the connecting edge 12e and the connecting wall surface 13h and between the connecting edge 13e and the connecting wall surface 12h occur synchronously while the orbiting scroll 13 makes a half turn. By the way, the fixed scroll 12 is provided with a compression chamber C having a high pressure after passing through the connecting wall surfaces 12h and 13h.
A communication path (introduction path) 30 for communicating (C ₀ ) with the groove 12l.
Is provided. The communication path 30 is formed by piercing the end plate 12a and the wall 12b, thereby forming the groove 1
A high-pressure fluid is introduced into the gap between the tip 2l and the tip seal 27d fitted in the groove 12l. The orbiting scroll 13 has a compression chamber C
A communication path (introduction path) 31 for communicating (C ₀ ) with the groove 131.
Is provided. The communication passage 31 is formed by piercing the end plate 13a and the wall 13b, thereby forming the groove 1
A high-pressure fluid is introduced into a gap between 3l and the tip seal 28d fitted in the groove 13l. The process of fluid compression at the time of driving the scroll compressor constructed as described above will be described in order with reference to FIGS. In the state shown in FIG. 5, the outer peripheral end of the wall 12b contacts the outer surface of the wall 13b, and
b comes into contact with the outer surface of the wall 12b, and the end plate 12
a, 13a, a fluid is sealed between the wall bodies 12b, 13b,
Two compression chambers C each having a maximum capacity are formed at positions directly opposite to each other with the center of the scroll compression mechanism therebetween. At this time, the connecting edge 12e and the connecting wall surface 13h are in sliding contact with each other, and the connecting edge 13e and the connecting wall surface 12h are in sliding contact with each other. From the state shown in FIG.
In the process of turning by 1/2 and reaching the state shown in FIG. 6, the compression chamber C advances toward the center while maintaining the closed state, gradually reducing the volume to compress the fluid, and the compression chamber preceding the compression chamber C. C ₀ also progresses toward the center while maintaining a sealed state, gradually decreasing the volume and continuously compressing the fluid. In this process, the sliding contact between the connecting edge 12e and the connecting wall surface 13h, and between the connecting edge 13e and the connecting wall surface 12h has been eliminated, and the two compression chambers C adjacent to each other with the wall body 13 therebetween are in communication with each other, and the pressure equalization is achieved. Is done. From the state shown in FIG.
In the process of turning by / 2 and reaching the state shown in FIG. 7, the compression chamber C advances toward the center while maintaining the sealed state, gradually reducing the volume and further compressing the fluid, and the compression chamber preceding the compression chamber C The chamber _C0 also moves toward the center while maintaining the sealed state, and gradually reduces the volume to continuously compress the fluid. Also in this process, the connection edge 12e, the connection wall surface 13h, and the connection edge 1
Sliding contact between 3e and the connecting wall surface 12h has been eliminated, and pressure equalization between two adjacent compression chambers C is continued. In the state shown in FIG. 7, a space c, which will later become a compression chamber, is formed between the inner surface of the wall 12b near the outer peripheral end and the outer surface of the wall 13b located inside the wall 12b. A space c, which will later become a compression chamber, is also formed between the inner surface of the wall 13b near the outer peripheral end and the outer surface of the wall 12b located inside the wall 13b. Flows in. At this time, the connecting edge 12e is connected to the connecting wall surface 13h.
Meanwhile, the connection edge 13e starts slidingly contacting the connection wall surface 12h, and the closed state of the compression chamber C preceding the space c is maintained. From the state shown in FIG.
In the process of turning by 1/2 and reaching the state shown in FIG.
Moves toward the center of the scroll compression mechanism while increasing the size, and the compression chamber C preceding the space c also advances toward the center while maintaining the sealed state, and gradually reduces the volume to compress the fluid. In this process, the sliding contact between the connecting edge 12e and the connecting wall surface 13h and between the connecting edge 13e and the connecting wall surface 12h are continued, and the space between the space c and the compression chamber C is kept sealed. In the process in which the orbiting scroll 13 is further turned by π / 2 from the state shown in FIG. 8 to the state shown in FIG. 5 again, the space c advances toward the center of the scroll compression mechanism while further expanding its size. , The compression chamber C preceding the space c also advances toward the center while maintaining a sealed state, gradually reducing the volume and compressing the fluid, and finally reaches the minimum volume. Also in this process, the sliding contact between the connecting edge 12e and the connecting wall surface 13h and between the connecting edge 13e and the connecting wall surface 12h is continued, and the space between the space c and the compression chamber C is kept in a sealed state. The change in the size of the compression chamber C from the maximum volume to the minimum volume (the volume when the discharge valve 26 is opened) is as follows: the compression chamber C in FIG. 5 → the compression chamber C in FIG. 6 → the compression chamber C in FIG. It can be regarded as the compression chamber C in FIG. Here, the expanded shape of the compression chamber in each state is shown in FIG. In the state (a) where the maximum volume is reached, the compression chamber is formed in a strip shape of an irregular shape whose width in the direction of the orbital axis becomes narrower on the way, and its width is equal to the bottom surface 1 at the outer peripheral end side of the scroll compression mechanism.
The wrap length Ll is substantially equal to the height of the wall 12b from 2g to the upper edge 12d (or the height of the wall 13b from the bottom 13g to the upper edge 13d), and the bottom 12f on the center side.
And a wrap length Ls (<Ll) substantially equal to the height from the top to the upper edge 12c (or the height of the wall 13b from the bottom surface 13f to the upper edge 13c). In the state (b), the compression chamber is shaped like an irregular strip whose width becomes narrower on the way as in the state (a).
As compared with the state shown in FIG. 7A, the length in the turning direction is shorter, the wrap length Ll is shorter, and the wrap length Ls is longer. In the state (c), the length of the compression chamber in the turning direction is further shortened by moving to the center side. In addition, the wrap length Ll disappears, resulting in a strip having a uniform width (wrap length Ls). In the state (d) where the volume is the minimum, the compression chamber has a strip shape having a uniform width as in the state (c).
The length in the turning direction is shorter than in the state of FIG. Thereafter, the discharge valve 26 is opened and the fluid is discharged. In the scroll compressor described above, the change in the volume of the compression chamber is caused not only by the decrease in the cross-sectional area parallel to the turning surface as in the conventional case, but also by the width in the turning axis direction as shown in FIG. Is caused synergistically by the reduction of the cross-sectional area. Therefore, the wall bodies 12b and 13b are stepped, and the wrap length of the wall bodies 12b and 13b is changed between the outer peripheral end and the center of the scroll compression mechanism to increase the maximum volume of the compression chamber C. By reducing the minimum volume or the like, the compression ratio can be improved as compared with a conventional scroll compressor in which the wrap length between the wall bodies is constant. In the scroll compressor, the communication passage 3 is provided between the groove 121 and the tip seal 27d.
0 internal pressure of the compression chamber C ₀ in the center side is introduced through, also between the grooves 13l and tip seal 28d, the inner pressure of the compression chamber C ₀ in the center side through the communication passage 31 is introduced. At this time, since the internal pressure of the compression chamber C ₀ located on the center side is much larger than the internal pressure of the compression chamber C located on the outer peripheral end side, the tip seals 27 d and 28 receive the pressure.
The pressing force of d is also increased, and the function as a seal can be sufficiently exhibited. As a result, the leakage of the fluid from the compression chamber C can be suppressed, so that the recompression power for the leakage is not required, and the driving efficiency can be improved by eliminating the power loss of the driving source. Next, a second embodiment of the scroll compressor according to the present invention will be described with reference to FIG. The components already described in the first embodiment are denoted by the same reference numerals, and description thereof is omitted. In the present embodiment,
A communication passage 32 for applying pressure to the tip seal 27 d on the fixed scroll 12 side is formed so as to communicate not with the compression chamber C but with the discharge cavity 23. Since the discharge cavity 23 communicates with the compression chamber C in which compression is most advanced and has the same internal pressure, in the case of the first embodiment in which the communication chamber 30 connects the compression chamber C and the groove 12l. The same effect can be obtained. As described above, according to the scroll compressor of the present invention, the portion between the outer edge of the upper edge of each wall and the seal member is provided through the introduction path. To
Although the internal pressure of the compression chamber located at the center or the space communicating with the compression chamber is introduced, the internal pressure is much larger than that of the compression chamber located at the outer peripheral end side. The pressing force is also increased, and the function as a seal is sufficiently exhibited. As a result, leakage of the fluid from the compression chamber can be suppressed, so that recompression power for the leakage is not required, and power loss of the driving source can be eliminated, and operation efficiency can be improved.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side sectional view showing a first embodiment of a scroll compressor according to the present invention. FIG. 2 is a perspective view of each of a fixed scroll and an orbiting scroll. FIG. 3 is a side sectional view showing a rib provided between an upper edge and a connection edge and a rib provided between a bottom surface and a connection wall surface. FIG. 4 is a cross-sectional view of a scroll compression mechanism combining a fixed scroll and an orbiting scroll. FIG. 5 is a state explanatory view showing a process of fluid compression when the scroll compressor is driven. FIG. 6 is a state explanatory view showing a process of fluid compression when the scroll compressor is driven. FIG. 7 is a state explanatory view showing a process of fluid compression when the scroll compressor is driven. FIG. 8 is a state explanatory view showing a process of fluid compression when the scroll compressor is driven. FIG. 9 is a state explanatory view showing a change in the size of the compression chamber from a maximum volume to a minimum volume. FIG. 10 is a view showing a second embodiment of the scroll compressor according to the present invention, and is a cross-sectional view of the scroll compression mechanism. DESCRIPTION OF SYMBOLS 12 Fixed scroll 12a End plate 12b Wall 12c, 12d Upper edge 12e Connection edge 12f Bottom 12h Connection wall 13 Orbiting scroll 13a End plate 13b Wall 13c, 13d Upper edge 13e Connection edge 13f Bottom 13h Connection wall 23 Discharge cavity (space) 30, 31, 32 Communication passage (introduction passage)

   ────────────────────────────────────────────────── ─── Continuation of front page    (72) Inventor Katsuhiro Fujita             3-1-1 Asahicho, Nishibiwajima-cho, Nishi-Kasugai-gun, Aichi Prefecture             Address Mitsubishi Heavy Industries, Ltd. F-term (reference) 3H039 AA02 AA06 AA12 BB15 BB28                       CC02 CC23 CC29 CC31

Claims (1)

Claims: 1. A fixed scroll fixed to a fixed position, having a spiral wall provided on one side surface of an end plate, and being provided on one side surface of the end plate. A revolving scroll having a spiral-shaped wall, and being supported so as to be able to revolve and revolve while interlocking the respective wall bodies while preventing rotation, and an upper edge of each of the wall bodies is divided into a plurality of portions. And the height of the portion is low at the center in the vortex direction and high at the outer peripheral end. Similarly, one side surface of each of the end plates corresponds to each of the portions, and the height is the vortex direction. In a scroll compressor having a stepped shape having a plurality of portions which are higher on the center side and lower on the outer peripheral end side, one or both of the fixed scroll and the orbiting scroll may include: Along the part located on the outer peripheral end side Seal member, and the internal pressure of the compression chamber defined by the portion located on the center side of one side surface of each end plate or the space communicating with the compression chamber, A scroll compressor, wherein an introduction path is provided between the portion located on the outer peripheral end side and the seal member.