JP2006177223A - Rotary two stage compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress deformation of an intermediate vessel accompanying pressure load and fastening load in a rotary two stage compressor and to reduce slide loss and leak loss of refrigerant or refrigerator oil. <P>SOLUTION: The rotary two stage compressor is provided with a rotary compression element provided with a low pressure compression element 20a and a high pressure compression element 20b provided with a rotary shaft including two eccentric parts and a roller revolved by eccentric rotation of the eccentric parts in each compression chamber with having a partition plate therebetween, and s delivery space of the low pressure compression chamber 20a separated from an inner space of a hermetic vessel. The delivery space 33 includes at least a bearing provided adjoining the low pressure compression element 20a and supporting a rotary shaft and a space between walls surrounding the bearing, opposes to the low pressure compression element 20a, includes a delivery space cover provided with a through hole keeping communication of the rotary shaft separating the delivery space 33 and an inner space of the hermetic vessel and supported by the bearing, and the inner space of the hermetic vessel. An elastic body is put between the delivery space cover and the bearing. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a rotary compressor used in an air conditioner equipped with a refrigeration cycle.

  Conventionally, as a rotary two-stage compressor used in a refrigeration cycle, for example, a structure disclosed in Japanese Patent Application Laid-Open No. 60-128990 (hereinafter referred to as Patent Document 1) is known. The compressor in this prior art is provided with an electric motor composed of a stator and a rotor at the upper part inside a sealed container. The rotating shaft connected to the electric motor has two eccentric portions. As a compression mechanism corresponding to these eccentric portions, a high-pressure compression element and a low-pressure compression element are provided inside the sealed container in order from the electric motor side.

  Each compression element revolves the roller by the eccentric rotation of the eccentric portion of the rotation shaft. The eccentric portions have a phase difference of 180 °, and the phase difference of the compression process of each compression element is 180 °. That is, the compression process of the two compression elements is in antiphase.

  The gas refrigerant, which is a working fluid, is sucked into the low pressure compression element at a low pressure Ps, is compressed, and rises to an intermediate pressure Pm. The gas refrigerant discharged at the intermediate pressure Pm passes through the discharge space and is discharged to the intermediate flow path. Next, the gas refrigerant having the intermediate pressure Pm is sucked into the high pressure compression element through the intermediate flow path and compressed to the high pressure Pd. The gas refrigerant discharged into the sealed container with the high pressure Pd flows down through the sealed container and is then discharged out of the compressor.

  As a structure of the discharge space of the rotary type two-stage compressor in which the internal pressure of such a sealed container is high, for example, a structure disclosed in Patent Document 1 is known. FIG. 10 is a cross-sectional view of a conventional rotary two-stage compressor.

  The compressor 100 includes a sealed container 13 including a bottom portion 21, a lid portion 12, and a body portion 22. An electric motor 14 having a stator 7 and a rotor 8 is provided above the inside of the sealed container 13. The rotating shaft 2 connected to the electric motor 14 includes two eccentric portions 5 and is pivotally supported by the main bearing 9 and the auxiliary bearing 19. In order from the motor 14 side with respect to the rotary shaft 2, a main bearing 9 having an end plate portion 9 a, a high pressure compression element 20 b, an intermediate partition plate 15, a low pressure compression element 20 a, and a sub bearing having an end plate portion 19 b. 19 are laminated and integrated by fastening elements 36 such as bolts.

  The end plate portion 9 b is fixed to the inner wall of the body portion 22 by welding and supports the main bearing 9. The end plate portion 19 b is supported by the sub bearing 19.

  Each compression element 20a and 20b is comprised as follows. The low pressure compression element 20a is composed of an end plate portion 19b of the auxiliary bearing 19, a cylindrical cylinder 10a, a cylindrical roller 11 fitted to the outer periphery of the eccentric portion 5a, and an intermediate partition plate 15 to form a compression chamber 23a. Is done. Further, the high pressure compression element 20b includes an end plate portion 9a of the main bearing 9, a cylindrical cylinder 10b, a cylindrical roller 11 fitted to the outer periphery of the eccentric portion 5b, and an intermediate partition plate 15, and a compression chamber 23b. Is composed.

  In these compression chambers 23a and 23b, flat vanes 18 (not shown in FIG. 10) connected to biasing force applying means such as coil springs rotate in accordance with the eccentric motion of the eccentric portions 5a and 5b. The compression chambers 23a and 23b are divided into a compression space and a suction space by moving forward and backward while contacting the outer periphery of the rollers 11a and 11b.

  The compression element 20 drives the roller 11 when the eccentric part 5 rotates eccentrically. As shown in FIG. 10, the eccentric portion 5a and the eccentric portion 5b have a phase difference of 180 °, and the phase difference in the compression process of the compression elements 20a and 20b is 180 °. That is, the compression process of the two compression elements is in opposite phase.

  The flow of the gas refrigerant that is the working fluid is represented by an arrow in FIG. The low-pressure Ps gas refrigerant supplied through the pipe 31 is sucked into the low-pressure compression element 20a from the suction port 25a connected to the pipe 31, and is compressed to the intermediate pressure Pm by the eccentric rotation of the roller 11a. When the discharge valve 28a that opens when the pressure in the compression chamber 23a reaches a preset pressure opens at the intermediate pressure Pm, the gas refrigerant that has reached the intermediate pressure Pm is discharged into the discharge space 33 that communicates with the discharge port 26a. . The discharge space 33 is a space that is isolated from the sealed space 29 in the sealed container 13 by the auxiliary bearing 19 and the cover 35, and the internal pressure thereof is basically the intermediate pressure Pm.

  The intermediate flow path 30 is a flow path that connects the discharge space 33 and the suction port 25b. One communicating space composed of the discharge space 33, the intermediate flow path 30, and the suction port 25b is an intermediate space that is separated from the hermetic container 13 and has an internal pressure Pm. Therefore, the gas refrigerant having the pressure Pm discharged from the discharge port 26a opened by the discharge valve 28a is discharged to the discharge space 33, and then communicates with the pressure chamber 23b of the high-pressure element 20b through the intermediate flow path 30. It reaches the suction port 25b.

  Next, the gas refrigerant having the intermediate pressure Pm passing through the intermediate flow path 30 and sucked into the high pressure compression element 20b from the suction port 25b is compressed to the high pressure Pd by the revolution of the roller 11b. When the discharge valve 28b that opens when the pressure in the compression chamber 23b reaches a preset pressure opens at high pressure Pd, the gas refrigerant is discharged from the discharge port 26b to the sealed space 29 that is the internal space of the sealed container 13. The gas refrigerant discharged into the sealed space 29 passes through the gap of the electric motor 14 and is discharged from the discharge pipe 27.

  The discharge space 33 is a circle that has a substantially concave intermediate container 19 that opens to the opposite side of the low-pressure compression element 20a with respect to the end plate portion 19b, and a through hole 40 in the center that closes the opening of the intermediate container 19. A plate-like cover 35 is provided.

  The intermediate container 19 includes an end plate portion 19b serving as one wall surface of the low-pressure side compression element 20a, a sub-bearing 19a that is located in the center of the end plate portion 19b and supports the rotary shaft 2, and a sub-bearing on the end plate portion 19b. An outer wall portion 19c located so as to surround the auxiliary bearing 19a on the outer peripheral side of 19a is integrally molded. The auxiliary bearing 19a and the outer wall portion 19c each have a contact surface that contacts the cover 35, and both contact surfaces are located at the same height, that is, on the same plane.

  With such a structure, the discharge space 33, which is an intermediate pressure, is partitioned from the high pressure internal space 29, and the gas compressed by the low pressure side compression element 20 a is discharged from the high pressure side compression element 20 b inside the container 13. A two-stage compression mechanism that establishes a path for introduction into the high-pressure side compression element 20b in a state separated from the gas and compresses the gas stepwise is possible.

JP-A-60-128990 (page 4, FIG. 1)

  In the structure of the discharge space 33 of the prior art, as shown in FIG. 11, a differential pressure (Pd−Pm) between the high pressure Pd and the intermediate pressure Pm acts from the outer surface of the cover 35, and transmits the pressure load to the sub bearing 19a. Due to the pressure load applied to the auxiliary bearing 19a, the center of the end plate portion 19b is deformed into a convex shape. Due to the deformation, there is a problem that the sliding loss between the end plate portion 19b and the roller 11a shown in FIG. 10 and the leakage loss of refrigerant or refrigerating machine oil from the same portion increase.

  In particular, as shown in FIG. 11, when the intermediate container 19 and the cover 35 are fastened by a fastening element 36 such as a bolt, an initial load at the time of assembly is also applied. When there is a difference in dimensional accuracy and surface accuracy between the contact surfaces of the sub-bearing 19a and the outer wall portion 19c, there is a problem that a tightening load is generated in the sub-bearing portion 19a and deformation of the end plate portion 19b increases.

  Further, when the tightening load of the fastening element 36 is strong, the outer wall portion 19c is also deformed. Therefore, in addition to the load on the auxiliary bearing portion 19a, the refrigerant or the refrigerator oil leaks between the outer wall portion 19c and the cover 35. There was a problem that loss increased.

  An object of the present invention is to suppress deformation due to a pressure load and a tightening load in an intermediate container forming a discharge space of a low-pressure side compression element, and to reduce a sliding loss. Furthermore, the deformation of the outer wall portion when the tightening load is strong is suppressed, and the leakage loss of refrigerant or refrigerating machine oil is reduced.

  In order to achieve the above object, a rotary compressor of the present invention includes an electric motor in a sealed container, a rotating shaft driven by the electric motor and having two eccentric parts, and a roller that revolves due to the eccentric rotation of the eccentric part. A low-pressure compression element and a high-pressure compression element provided in the compression chamber, respectively, and a rotary compression element provided via a partition plate; and a discharge space of the low-pressure compression element separated from the internal space of the sealed container. ing. The discharge space has at least a space between a bearing provided adjacent to the low pressure compression element and supporting the rotating shaft and a wall surrounding the bearing, and the discharge space is provided in the low pressure compression element. A discharge space cover provided with a through hole through which the rotary shaft pivotally supported by the bearing and the inner space of the sealed container communicates with the discharge space and the inner space of the sealed container facing each other. The discharge space cover and the bearing are via an elastic body.

  Further, when the tightening load is strong, at least one reinforcing support portion having, for example, a substantially rectangular cross-sectional shape is connected so as to connect the auxiliary bearing and the outer wall portion, and the height of the support portion is set to the bearing. It was lower than the top of the wall that surrounds.

  Further, as the elastic body, a substantially frustoconical disc spring having a bottom surface on the discharge space cover side or a disc-shaped gasket may be used.

  Further, in order to reduce the influence of the tightening load, the fastening element for fastening the discharge space cover to the intermediate space is arranged on the circumference of the diameter φDp with respect to the axis center of the rotating shaft, and the diameter φDp is set to the maximum of the bearing. The range may be (φd + φD) / 2 ≦ φDp ≦ φD with respect to the outer diameter φd and the maximum inner diameter φD of the wall surrounding the periphery of the bearing.

  According to the present invention, the sliding loss in the low-pressure side compression element can be reduced, or the leakage loss of refrigerant or refrigerating machine oil can be reduced, which contributes to the improvement of the performance of the rotary compressor.

  An embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a rotary two-stage compressor according to this embodiment. In FIG. 1, parts and members equivalent to those in FIG.

  The compressor 1 includes a sealed container 13 including a bottom portion 21, a lid portion 12, and a body portion 22. An electric motor 14 having a stator 7 and a rotor 8 is provided above the inside of the sealed container 13. The rotating shaft 2 connected to the electric motor 14 includes two eccentric portions 5 and is pivotally supported by the main bearing 9 and the auxiliary bearing 19a. Ends shared with the main bearing 9, the high pressure compression element 20b, the intermediate partition plate 15, the low pressure compression element 20a, and the low pressure compression element 20a provided with an end plate portion 9a in order from the motor 14 side with respect to the rotating shaft 2. A concave intermediate container 19 composed of a plate portion 19b, an outer wall portion 19c, and a sub-bearing 19a is laminated and integrated with a fastening element 36 such as a bolt.

  The end plate portion 9 a is fixed to the inner wall of the body portion 22 by welding and supports the main bearing 9. The end plate portion 19b is supported by the auxiliary bearing 19a. In the present embodiment, the end plate portion 19b is fixed by the fastening element 36, but may be fixed to the body portion 22 by welding.

  Each compression element 20a and 20b is comprised like FIG. 1, FIG. In the low-pressure compression element 20a, a compression chamber 23a is constituted by an end plate portion 19b, a cylindrical cylinder 10a, a cylindrical roller 11a fitted to the outer periphery of the eccentric portion 5a, and the intermediate partition plate 15. In the high-pressure compression element 20b, a compression chamber 23b is composed of an end plate portion 9a, a cylindrical cylinder 10b, a cylindrical roller 11b fitted to the outer periphery of the eccentric portion 5b, and an intermediate partition plate 15. .

  These compression chambers 23a, 23b are rollers 11a, 11b in which a flat vane 18 connected to an urging force applying means (not shown) such as a coil spring rotates in accordance with the eccentric motion of the eccentric portions 5a, 5b. The compression chambers 23a and 23b are divided into a compression space and a suction space by moving back and forth while contacting the outer periphery of the compression chamber 23a.

  The compression element 20 drives the roller 11 when the eccentric part 5 rotates eccentrically. As shown in FIGS. 1 and 2, the eccentric portion 5a and the eccentric portion 5b have a phase difference of 180 °, and the phase difference in the compression process of the compression elements 20a and 20b is 180 °. That is, the compression process of the two compression elements is in opposite phase.

  The flow of the gas refrigerant which is a working fluid is represented by an arrow in FIG. The low-pressure Ps gas refrigerant supplied through the pipe 31 is sucked into the low-pressure compression element 20a from the suction port 25a connected to the pipe 31, and is compressed to the intermediate pressure Pm by the eccentric rotation of the roller 11a. When the discharge valve 28a that opens when the pressure in the compression chamber 23a reaches a preset pressure opens at the intermediate pressure Pm, the gas refrigerant that has reached the intermediate pressure Pm is discharged into the discharge space 33 that communicates with the discharge port 26a. . The discharge space 33 is a space that is provided adjacent to the compression element 20a for low pressure, and is isolated from the sealed space 29 in the sealed container 13 by the cover 35 and the elastic body 37 that cover the intermediate container 19, the discharge space 33, The internal pressure is basically the intermediate pressure Pm. The intermediate flow path 30 is a flow path that connects the discharge port 26c from the discharge space 33 and the suction port 25b. After the gas refrigerant having the pressure Pm discharged from the discharge port 26a opened by the discharge valve 28a is discharged to the discharge space 33, the gas refrigerant passes through the discharge port 26c and the intermediate flow path 30, and the pressure chamber 23b of the high-pressure element 20b. The suction port 25b communicates.

  Next, the gas refrigerant having the intermediate pressure Pm passing through the intermediate flow path 30 and sucked into the high pressure compression element 20b from the suction port 25b is compressed to the high pressure Pd by the revolution of the roller 11b. When the pressure in the compression chamber 23b reaches a preset pressure, the opening discharge valve 28b opens at a high pressure Pd. The gas refrigerant is discharged from the discharge port 26b to the sealed space 29 that is the internal space of the sealed container 13. The gas refrigerant discharged into the sealed space 29 passes through the gap of the electric motor 14 and is discharged from the discharge pipe 27.

  FIG. 3 is a longitudinal sectional view of the discharge space 33, and FIG. 4 is a bottom view of the intermediate container 19. The intermediate space 33 is configured by fastening the intermediate container 19, the cover 35, and the elastic body 37 with a fastening element 36. The elastic body 37 is sandwiched between the flat surface 19 d and the cover 35.

  The intermediate container 19 is a cast or iron-based sintered member, and the auxiliary bearing 19a, the end plate portion 19b, and the outer wall portion 19c are integrally molded. The end plate portion 19a has a flat plate shape and includes a discharge hole 26a from the compression element 20a for low pressure and a base 38 for installing the discharge valve 28a shown in FIG.

  The intermediate container 19 has a substantially concave shape opened in the direction of the cover 35 on the opposite side to the compression element 20a for low pressure, and the outer wall portion 19c contacts the cover 35 in parallel with the end plate portion 19b by molding, cutting or polishing. It has a contact surface.

  The outer wall portion 19 c has a substantially cylindrical shape with a maximum inner diameter of φD, and includes a through hole 39 for the fastening element 36 and a discharge port 25 c communicating with the discharge port 30 connected to the intermediate flow path 30. Since the through-hole 39 is provided inside the outer wall portion 19c, it has a petal shape. In other words, the stress from the fastening element 36 applied to the through hole 39 can be transmitted by the structure continuous with the outer wall portion 19c.

  Four or more through holes 39 are provided on the circumference of the diameter φDp substantially uniformly in the circumferential direction. The diameter φDp was in the range of (φD + φd) / 2 ≦ φDp ≦ φD with respect to the diameter φD and the maximum outer diameter φd of the sub-bearing 19a described later.

  The auxiliary bearing 19a has a substantially cylindrical shape with a maximum outer diameter φd. The outer diameter side has a stepped shape and is provided with a flat surface 19 d facing the cover 35. The flat surface 19d is a flat surface that is lower in height than the outer wall portion 19c and is cut and provided over the entire circumference of the auxiliary bearing 19a. The flat surface 19d is provided at a position where a predetermined gap is obtained between the flat surface 19d and the cover 35.

  The auxiliary bearing 19a has a stepped inner diameter side, and includes a contact portion 19e that supports the rotating shaft 2 shown in FIG. 1 and a non-contact portion 19f that has a larger diameter than the contact portion 19e and does not support the rotating shaft 2. . Here, the flat surface 19d is provided not on the contact portion 19e but on the outer peripheral portion of the non-contact portion 19f. The flat surface 19d is formed integrally with the intermediate container 19, but machining such as cutting may be used.

  As shown in FIG. 5, the cover 35 is a disk-shaped member that is stamped and formed by pressing. The outer diameter of the cover 35 was made larger than the maximum inner diameter φD of the intermediate container 19. However, the flat surface contacting the outer wall portion 19c may be cut or polished. The cover 35 was provided with the same number and the same number of through holes 39 for the fastening elements 36 as the through holes 39 of the intermediate container 19. A central hole 40 is provided in the center of the cover 35 so as to pass the rotary shaft 2 of FIG. 1 or the tip of the auxiliary bearing 19a. The diameter of the central hole 40 is smaller than the maximum diameter φd of the auxiliary bearing 19a.

  Moreover, as shown in FIG. 6, the elastic body 37 is a disc spring having a substantially truncated cone shape in the present embodiment. The disc spring was formed by pressing a copper member. The elastic body 37 is installed on the flat surface 19d through the tip of the auxiliary bearing 19a.

  At that time, as shown in FIG. 3, the bottom surface of the elastic body 37 is set to the cover 35 side. Providing the bottom surface side of the substantially truncated cone having a large radius so as to contact the cover 35 makes it possible to provide a wide sealing area (seal area) between the parts as opposed to providing the cover 35 in the opposite direction.

  The elastic body 37 may be a disc-shaped gasket as shown in the cross-sectional view of FIG. In the case of a gasket, a rubber material or a resin material is used so that it can be more easily deformed.

  With the above configuration, the outer wall portion 19c and the cover 35 are in surface contact to ensure sealing performance. On the other hand, the gap between the flat surface 19 and the cover 35 ensures sealing performance by the elastic body 37 being deformed and closely adhered. This shape suppresses deformation of the end plate portion 19b because the elastic body 37 is deformed even when the cover 35 receives a pressure load as shown in FIG. 11 due to external pressure. Furthermore, even if a processing error occurs between the outer wall portion 19c and the flat surface 19d, the deformation of the end plate portion 19b can be suppressed while ensuring the sealing performance.

  Further, since the arrangement of the through holes 39 is (φD + φd) / 2 ≦ φDp ≦ φD, the fastening load from the fastening element 36 is transmitted as a vertical stress to the rigid outer wall portion 19c, and the load is transmitted to the auxiliary bearing 19a. ease. Therefore, even when the tightening load is strong, the deformation of the end plate portion 19b due to the load from the auxiliary bearing 19a can be suppressed.

  Further, since the flat surface 19d is provided on the non-contact portion 19f side, even if a load is applied to the flat surface 19d, the auxiliary bearing 19a can be relaxed by deformation in the radial direction, and deformation of the end plate portion 19b and the contact portion 19e is suppressed. To do.

  Further, since the auxiliary bearing 19a has a stepped shape, positioning of the elastic body 37 during assembly can be facilitated, and displacement of the elastic body 37 can be prevented.

  Next, application examples of the present embodiment will be described with reference to FIGS. 8 is a bottom view of the intermediate container 19 of the present embodiment, and FIG. 9 is a cross-sectional view taken along the line AA of FIG. Between the outer wall portion 19c and the auxiliary bearing 19a, three beams 41 which are support portions having a substantially rectangular cross-sectional shape are provided.

  The beam 41 was provided along a straight line connecting the center of the through hole 39 and the center of the auxiliary bearing 19a. This is to increase the rigidity around the through hole 39 so as to further reduce the load on the fastening element 36. Although at least one beam 41 as the support portion may be provided, the effect is further enhanced by providing the beam 41 for each through hole 39 as shown in the figure.

  As shown in FIG. 9, the beam 41 has a height lower than that of the outer wall portion 19c and substantially the same height as the flat surface 19d. However, the height of the beam 41 may be lower than the flat surface 19d. The discharge port 25c is provided so as to communicate with the same space as the discharge port 26a among the three spaces partitioned by the beam 41.

  With this structure, the deformation of the outer wall portion 19c due to the tightening load is suppressed, and the sealing performance between the outer wall portion 19c and the cover 35 is further improved. Since the height of the long side portion which is one end of the beam 41 is made lower than the top portion of the outer wall portion 19b, the transmission of the load from the cover 35 to the end plate portion 19b by the beam 41 does not increase. That is, it is possible to suppress deformation of the outer wall portion 19c while suppressing an increase in deformation of the end plate portion 19b.

  Furthermore, the beam 41 does not become a fluid obstacle due to the position of the discharge port 25c. That is, an increase in fluid loss due to the beam 41 is suppressed.

  As mentioned above, this embodiment suppresses the deformation | transformation by the pressure load and clamping | tightening load in the intermediate | middle container which forms the discharge space of a low voltage | pressure side compression element, and reduces a sliding loss. Furthermore, the deformation of the outer wall portion when the tightening load is strong is suppressed, and the leakage loss of refrigerant or refrigerating machine oil is reduced.

1 is a cross-sectional view of a rotary two-stage compressor showing an embodiment of the present invention. 1 is a configuration diagram of a rotary two-stage compressor showing an embodiment of the present invention. The longitudinal cross-sectional view of the intermediate space of this embodiment. The bottom view of the intermediate container of this embodiment. The bottom view of the cover of this embodiment. Sectional drawing of the elastic body of this embodiment. Sectional drawing of the gasket of this embodiment. The longitudinal cross-sectional view of the intermediate space which is an application example of this embodiment. AA sectional drawing of FIG. The longitudinal cross-sectional view of the rotary type two stage compressor of a prior art. The figure showing the load and deformation | transformation in the intermediate space of a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Rotating shaft, 5 ... Eccentric part, 9 ... Main bearing, 10 ... Cylinder, 11 ... Roller, 19 ... Intermediate container, 20 ... Compression element, 30 ... Intermediate flow path, 33 ... Discharge space, 35 ... cover, 37 ... elastic body.

Claims (8)

A low-pressure compression element and a high-pressure compression element each having an electric motor in a sealed container, a rotating shaft driven by the electric motor and having two eccentric portions, and a roller that revolves by the eccentric rotation of the eccentric portion. The low-pressure compression element separated from the rotary compression element provided via an intermediate partition plate, the compression chamber of the low-pressure compression element and the internal space of the hermetic container connected to the compression chamber of the high-pressure compression element A rotary two-stage compressor having a discharge space from
The discharge space has at least a space between a bearing provided adjacent to the low pressure compression element and supporting the rotary shaft and a wall surrounding the bearing, and faces the low pressure compression element. And a discharge space cover provided with a through-hole through which the rotary shaft pivotally supported by the bearing and the inner space of the sealed container communicates with the discharge space and the inner space of the sealed container. The space type cover and the bearing are a rotary type two-stage compressor through an elastic body.   2. The rotary two-stage compressor according to claim 1, wherein at least one support portion is provided between the bearing and the wall portion.   3. The rotary two-stage compressor according to claim 2, wherein one end portion of the support portion is located closer to the low-pressure compression element than a top portion of the wall. 4.   3. The rotary two-stage compressor according to claim 2, wherein a hole through which a fastening element that fastens the discharge space cover to the intermediate space passes is provided between the wall and the bearing, and the support portion includes the hole and the hole. A rotary two-stage compressor provided between the bearings.   2. The rotary type two-stage compressor according to claim 1, wherein the discharge space having an end plate portion which is a part of the low pressure compression element and has the wall is provided with the bearing inside and the end. An intermediate container having an opening in the direction facing the low-pressure compression space by the plate portion and the wall and the discharge space cover, and the bearing is provided with a flat surface facing the discharge space cover, A rotary two-stage compressor in which the elastic body is provided between the flat surface and the cover.   2. The rotary two-stage compressor according to claim 1, wherein the elastic body is a substantially frustoconical disc spring having a bottom surface on the discharge space cover side or a disc-shaped gasket.   2. The rotary type two-stage compressor according to claim 1, wherein a fastening element that fastens the discharge space cover to the intermediate space is disposed on a circumference of a diameter φDp with respect to an axis center of the rotating shaft, and the diameter φDp A rotary two-stage compressor in which (φd + φD) / 2 ≦ φDp ≦ φD with respect to the maximum outer diameter φd of the bearing and the maximum inner diameter φD of the wall. 2. The rotary two-stage compressor according to claim 1, wherein the elastic body is arranged in a space between the discharge space cover and the bearing.

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