JP2013245642A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the problem of so far reducing compressor performance due to increasing deformation of a cylinder, since rigidity of a fitting cylinder part increases by the presence of an extended cylinder part, when a liner has the extended cylinder part on the cylinder chamber side from the fitting cylinder part fitted to the cylinder, in a constitution for pressing the liner in a suction passage of the cylinder.SOLUTION: A liner 14 for guiding a refrigerant in a cylinder chamber 15, has a fitting cylinder part 14a of an outer diameter slightly larger than an inner diameter of a suction passage 19 formed with a cylinder 5 of a compression mechanism 102, and constitutes a seal part by closely fitting the fitting cylinder part 14a and the suction passage 19 by being pressed in the suction passage 19. The liner 14 also has an extended cylinder part 14b extended in the cylinder chamber 15 direction by continuing with the fitting cylinder part 14a, and the extended cylinder part 14b is constituted so that the rigidity reduces more than the fitting cylinder part 14a.

Description

  The present invention relates to a compressor used in an air conditioner, a refrigerator, a blower, a water heater, and the like.

  An example of a conventional configuration will be described with reference to a longitudinal sectional view of a rotary type high pressure type hermetic compressor 500 of FIG.

  A suction chamber and a compression chamber are formed by sandwiching a cylinder 504, a rolling piston 541, and a vane (not shown) between the upper bearing 505a and the lower bearing 505b, and the rolling piston 541 rotates as the drive shaft 523 rotates. A compression mechanism 503 that performs a compression operation, a rotor 521 that transmits a rotational force to the drive shaft 523, and an electric element 502 that includes a stator 522 are housed in an airtight container 501.

  A suction liner 509 is connected to a suction hole 506 provided in the cylinder 504.

  The low-temperature and low-pressure intake refrigerant gas is compressed by the compression mechanism 503 and discharged into the sealed container 501 as a high-temperature and high-pressure discharged refrigerant gas. After the oil mist contained in the discharged refrigerant gas is separated inside the sealed container 501, To the outside of the compressor from a discharge pipe 511 provided in the compressor.

  12 is an enlarged view of a portion where the suction liner 509 of FIG. 11 is attached.

  A suction liner 509 is press-fitted into a suction hole 506 provided in the cylinder 504, and a suction connection pipe 508 is inserted on the upstream side of the suction liner 509. ing. The low-temperature and low-pressure suction refrigerant gas flows into the compression mechanism 503 via the suction connection pipe 508, the suction liner 509, and the suction hole 506. On the other hand, the outside atmosphere of the compression mechanism 503 and the outside of the suction liner 509 are filled with high-temperature and high-pressure discharged refrigerant gas. The inside of the suction hole 506 and the outside of the suction liner 509 prevent the high-pressure refrigerant gas from flowing into the suction pipe path by the press-fitting portion 591 serving as a partition.

  However, since the compression mechanism 503 exposed to the high-temperature and high-pressure discharged refrigerant gas is in a high temperature state and the wall surface of the suction hole 506 is also high temperature, the low-temperature suction refrigerant gas is heated when passing through the suction hole 506. There is a problem that the density is lowered, and as a result, the volumetric efficiency and the compressor efficiency of the compressor are lowered.

  In order to solve this problem, in the high-pressure dome type compressor shown in Patent Document 1, as shown in FIG. 13, a fitting cylinder portion 510 a tightly fitted in the suction hole 506 and a fitting cylinder portion are fitted in the suction hole 506 of the cylinder 504. A suction liner 510 having a small diameter cylindrical portion 510b that is continuous with 510a and having a smaller diameter than the inner diameter of the suction hole 506 is attached, and the outer peripheral surface of the small diameter cylindrical portion 510b of the suction liner 510 and the inner peripheral surface of the suction hole 506 are By providing the gas retention part P <b> 1 therebetween, the low-temperature and low-pressure suction refrigerant gas is suppressed from being heated by the heat of the cylinder 504.

Japanese Utility Model Publication No. 5-993

  However, in the conventional configuration of Patent Document 1, since the small-diameter cylindrical portion 510b is present, the fitting is closer at the boundary between the fitting cylindrical portion 510a and the small-diameter cylindrical portion 510b than when the small-diameter cylindrical portion 510b is not present. The deformation of the cylindrical portion 510a is hindered by the small diameter cylindrical portion 510b. That is, the rigidity of the fitting tube portion 510a is increased by the presence of the small diameter tube portion 510b. For this reason, since the fitting cylinder part 510a becomes difficult to deform | transform, the stress which acts on the cylinder 504 in the press-fit part 591 becomes large, and the deformation | transformation of the cylinder 504 becomes large. As a result, deformation to the sliding portion of the compression mechanism 503 occurs and sliding loss increases, and there is a problem that the compressor input increases and the performance of the compressor deteriorates.

  In order to solve the above problems, a compressor according to the present invention includes a sealed container, a compression mechanism disposed in the sealed container, a suction passage formed in the compression mechanism and through which a refrigerant passes, and the suction passage. A liner that is press-fitted into the fitting tube, a fitting cylinder portion having an outer diameter formed slightly larger than an inner diameter of the suction passage, an extension cylinder portion formed continuously from the fitting cylinder portion, The extension cylinder part is configured to have a lower radial rigidity than the fitting cylinder part.

  As a result, the radial rigidity of the extension cylinder part is configured to be lower than that of the fitting cylinder part, so that the influence of the rigidity of the extension cylinder part on the rigidity of the fitting cylinder part is small. The rise can be suppressed.

  In the compressor of the present invention, when the liner is press-fitted into the suction passage, the deformation acting on the compressor portion such as the cylinder due to the fitting cylinder portion is not significantly increased, and deformation of the sliding portion is suppressed. Thus, the compressor performance can be prevented from deteriorating.

1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1 of the present invention. Sectional drawing in the AA cross section of the rotary compressor shown in FIG. Sectional drawing in the BB cross section of the rotary compressor shown in FIG. Configuration diagram of liner 14 in Embodiment 1 of the present invention Configuration diagram of liner 14 in Example 1 of Embodiment 1 of the present invention Configuration diagram of liner 14 in Example 2 of Embodiment 1 of the present invention Configuration diagram of liner 14 in Example 3 of Embodiment 1 of the present invention Vertical sectional view of a rotary compressor according to Embodiment 2 of the present invention Sectional drawing in CC cross section of the rotary compressor shown in FIG. Sectional drawing in the DD cross section of the rotary compressor shown in FIG. Configuration of conventional compressor Fig. 11 is an enlarged view of the installation area of the inhalation liner in Fig. 11. Configuration diagram showing configuration of conventional liner disclosed in Patent Document 1

A first invention includes a sealed container, a compression mechanism disposed in the sealed container, a suction passage formed in the compression mechanism through which a refrigerant passes, a liner press-fitted into the suction passage, and the liner A fitting cylinder part having an outer diameter formed slightly larger than an inner diameter of the suction passage, and an extension cylinder part formed continuously from the fitting cylinder part, and the extension cylinder part is The compressor is configured so that the radial rigidity is lower than that of the fitting cylinder part, and an increase in the rigidity of the fitting cylinder part due to the presence of the extension cylinder part in the liner fits the rigidity of the extension cylinder part. Since it can suppress by lowering than that of a joint cylinder part, the effect | action of the stress to the compression mechanism by press injection of a liner is reduced, and a deformation | transformation of a compression mechanism can be suppressed. As a result, it is possible to suppress deformation of the compressor sliding portion, and it is possible to prevent deterioration in compressor performance and reliability due to an increase in sliding loss.

  In the compressor according to the first aspect of the present invention, in particular, in the compressor of the first aspect, the thickness of the tube wall of the extension tube portion is smaller than the thickness of the tube wall of the fitting tube portion in a cross section perpendicular to the liner length direction Since the rigidity of the part with small thickness is reduced, the rigidity of the extension cylinder part as a whole is also reduced, and the increase in the rigidity of the fitting cylinder part is suppressed to reduce the compressor performance. Can be prevented. Moreover, by doing in this way, the rigidity of a length direction can be maintained, reducing the rigidity of a radial direction, Therefore The fall of the reliability by the rigidity reduction of an extension cylinder part can be prevented.

  According to a third aspect of the present invention, in particular, in the first or second aspect of the invention, by forming a groove in the length direction of the liner on the surface of the tube wall of the extension tube portion, the thickness of the bottom portion of the groove is reduced. Because it is thin and the rigidity is reduced, the rigidity of the extension cylinder part is reduced, and the increase in the rigidity of the fitting cylinder part is suppressed, and it can be implemented by applying the existing technology for manufacturing a grooved tube. Development costs can be reduced.

  A fourth invention is a compressor having a convex portion formed in a corrugated shape toward the outside in the radial direction of the tube wall of the extension cylinder portion, particularly in either the first or second invention. Since the stress generated in the circumferential direction of the extension cylinder part by the external force acting in the radial direction of the extension cylinder part can be elastically deformed and absorbed like a spring in a wavy shape, the rigidity of the fitting cylinder part can be absorbed. By suppressing the increase, it is possible to suppress the deformation of the cylinder and the like and to prevent the compressor performance from being lowered. Further, since the convex portion serves as a rib in the length direction of the liner and the rigidity in the length direction is increased, the reliability of the liner is improved.

  In a fifth aspect of the invention, in particular, in the first aspect of the invention, the thickness of the extension tube portion is a compressor formed thinner than the tube wall thickness of the fitting tube portion, and extends beyond the thickness of the fitting tube portion. Since the rigidity of the extension cylinder part is relatively low because the thickness of the cylinder part is thinner, the rigidity of the fitting cylinder part is not significantly increased, and the deformation of the compressor constituent member such as the cylinder is suppressed, and the compressor A decrease in performance can be prevented. Moreover, since it can implement only by making thickness of an extension cylinder part thin, new technical development, such as a shaping | molding method, is unnecessary, and development cost can be reduced.

  In a sixth aspect of the present invention, in particular, in the first aspect, the extension tube portion is made of a material different from the fitting tube portion, and the material forming the extension tube portion is softer than the material forming the fitting tube portion. By configuring the extension cylinder portion with a different material, the rigidity can be reduced to a range that cannot be realized only by changing the shape of the same material. As a result, the rigidity of the extension cylinder part can be more effectively reduced and the rigidity of the fitting cylinder part can be prevented from increasing, so that the deformation of the compressor constituent members can be reduced and the deterioration of the compressor performance can be prevented. Is possible.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by the following embodiment.

(Embodiment 1)
As shown in FIG. 1, the rotary compressor 100 of the present embodiment includes a sealed container 1, a motor 2, a compression mechanism 102, and a shaft 4. The compression mechanism 102 is disposed at the lower part of the sealed container 1. The motor 2 is disposed on the compression mechanism 102 inside the sealed container 1. The compression mechanism 102 and the motor 2 are connected by the shaft 4. A terminal 21 for supplying electric power to the motor 2 is provided on the top of the sealed container 1. An oil reservoir 22 for holding lubricating oil is formed at the bottom of the sealed container 1.

  The motor 2 includes a stator 17 and a rotor 18. The stator 17 is fixed to the inner wall of the sealed container 1. The rotor 18 is fixed to the shaft 4 and rotates together with the shaft 4.

  A discharge pipe 11 is provided on the top of the sealed container 1. The discharge pipe 11 penetrates the upper part of the sealed container 1 and opens toward the internal space 13 of the sealed container 1. The discharge pipe 11 serves as a discharge flow path that guides the refrigerant compressed by the compression mechanism 102 to the outside of the sealed container 1. During the operation of the rotary compressor 100, the internal space 13 of the sealed container 1 is filled with the compressed refrigerant. That is, the rotary compressor 100 is a high-pressure shell type compressor. According to the high-pressure shell type rotary compressor 100, the motor 2 can be cooled with the refrigerant, so that improvement in motor efficiency can be expected.

  The compression mechanism 102 is driven by the motor 2 so as to compress the refrigerant. Specifically, the compression mechanism 102 includes a compression block 3, an upper bearing 6, a lower bearing 7, and a muffler 9. The refrigerant is compressed by the compression block 3. The compression block 3 is immersed in oil stored in the oil reservoir 22.

  FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1 and shows the configuration of the compression block 3. In FIG. 2, the compression block 3 includes a cylinder 5, a piston 8, a vane 32, a suction passage 19, a discharge hole 40, and a spring 36.

  The shaft 4 has an eccentric part 4a. The eccentric portion 4 a protrudes outward in the radial direction of the shaft 4. The piston 8 is disposed inside the cylinder 5. Inside the cylinder 5, a piston 8 is attached to the eccentric portion 4a.

  The upper bearing 6 and the lower bearing 7 are attached to the cylinder 5 so as to form a cylinder chamber 15 between the inner peripheral surface of the cylinder 5 and the outer peripheral surface of the piston 8. Specifically, the upper bearing 6 is attached to the upper part of the cylinder 5, and the lower bearing 7 is attached to the lower part of the cylinder 5. The liner 14 is brazed to the suction outer tube 46 fixed to the sealed container 1, and a gap generated between the suction outer tube 46 and the liner 14 is sealed.

  The suction passage 19 is formed in the cylinder 5. The suction passage 19 opens toward the cylinder chamber 15 and forms a suction port 20. A liner 14 is connected to the other end of the suction passage 19.

  The discharge hole 40 is formed in the upper bearing 6. The discharge hole 40 opens toward the cylinder chamber 15. A discharge valve 43 is provided in the discharge hole 40 so as to open and close the discharge hole 40.

  The vane groove 34 is arranged so that a vane (blade 32) having a circular arc shape at the tip that comes into contact with the piston 8 can slide. The vane 32 partitions the cylinder chamber 15 along the circumferential direction of the piston 8. Thereby, the cylinder chamber 15 is partitioned into the suction chamber 25a and the discharge chamber 25b.

  The suction passage 19 and the discharge hole 40 are located on the left and right of the vane 32, respectively. Through the suction passage 19, the refrigerant to be compressed is supplied to the cylinder chamber 15 (suction chamber 25a). The refrigerant compressed in the cylinder chamber 15 pushes open the discharge valve 43 and is discharged from the discharge chamber 25 b through the discharge hole 40.

  The piston 8 and the vane 32 may be constituted by a single part, that is, a swing piston. The vane 32 may be coupled to the piston 8.

  A spring 36 is disposed behind the vane 32. The spring 36 pushes the vane 32 toward the center of the shaft 4. A rear portion of the vane groove 34 communicates with the internal space 13 of the sealed container 1. Accordingly, the pressure in the internal space 13 of the sealed container 1 is applied to the back surface of the vane 32. Further, the lubricating oil stored in the oil reservoir 22 is supplied to the vane groove 34.

  As shown in FIG. 1, the muffler 9 is attached to the upper bearing 6 so as to form a refrigerant discharge space 51 in which the refrigerant discharged from the discharge chamber 25 b through the discharge hole 40 can stay on the opposite side of the cylinder chamber 15. Yes. Specifically, the muffler 9 is attached to the upper part of the upper bearing 6 so that the refrigerant discharge space 51 is formed above the upper bearing 6. The discharge valve 43 is covered with the muffler 9. The muffler 9 is formed with a discharge hole 9 a for guiding the refrigerant from the refrigerant discharge space 51 to the internal space 13 of the sealed container 1. The refrigerant discharge space 51 serves as a refrigerant flow path. The shaft 4 passes through the center of the muffler 9 and is rotatably supported by the upper bearing 6 and the lower bearing 7.

  FIG. 3 is a cross-sectional view taken along line BB in FIG. The liner 14 has a fitting cylinder portion 14a having an outer diameter dL1 that is formed slightly larger than the inner diameter dc of the suction passage 19, and extends further downstream of the refrigerant flow than the fitting cylinder portion 14a. An extension cylinder portion 14b having an outer diameter that is smaller than the inner diameter dc is provided. A difference Δd (dL1−dc) between the outer diameter dL1 of the fitting cylinder portion 14a and the inner diameter dc of the suction passage 19 is called a press-fitting allowance, and is usually set to several tens of μm. By press-fitting the liner 14 into the suction passage 19, the fitting cylindrical portion 14 a having a press-fitting allowance is fitted with the suction passage 19 without gaps, and a seal region 45 is configured. The presence of the seal region 45 isolates the internal space of the sealed container 1 and the downstream space from the seal region 45 of the suction passage 19, and the discharged refrigerant in the sealed container 1 and the suction refrigerant flowing into the suction passage 19 are separated. Prevents mixing. The extension cylinder part 14b exists downstream of the fitting cylinder part 14a, and its outer diameter dL2 is smaller than the inner diameter dc of the suction passage 19, so that it is fixed with a distance from the inner wall of the suction passage 19 Has been. The space between the extended cylindrical portion 14b and the inner wall of the suction passage 19 serves as a retention space 61 in which the refrigerant is retained. By acting as a heat insulating layer, the amount of heat input to the suction passage 19 from the outside of the cylinder 5 is reduced. ing.

  FIG. 4 shows the cross-sectional shape in the length direction of the liner 14 and the axial shape of the extension tube portion 14b. A groove 14c in the length direction is formed on the outer peripheral portion of the extension cylinder portion 14b. The cross-sectional shape of the groove 14c is rectangular, and is formed from the end of the extension cylinder part 14b to the vicinity of the boundary line with the fitting cylinder part. Four grooves 14c are formed at an angle of 90 degrees on the outer periphery of the extended cylindrical portion 14b.

  When the liner 14 is press-fitted into the cylinder 5, deformation and stress are generated around the fitting cylinder portion 14a. Specifically, since the outer diameter of the fitting cylinder portion 14a of the liner 14 is larger than the inner diameter of the suction passage 19 by a press-fit allowance Δd, the fitting cylinder portion 14a press-fits the suction passage 19 in a press-fit manner. As a result, the cylinder 5 is deformed. Therefore, the deformation amount of the cylinder 5 depends on the rigidity of the liner 14 and the press-fitting allowance Δd. When the amount of deformation is large, the deformation to the sliding portion becomes remarkable, and the compressor input increases or it becomes difficult to maintain the reliability.

Since the fitting cylinder part 14a is continuous with the extension cylinder part 14b, its rigidity is also influenced by the rigidity of the extension cylinder part 14b. When the extension cylinder part 14b exists, the rigidity of the fitting cylinder part 14a will rise from the case where it does not exist. Therefore, when the liner 14 having the extension cylinder portion 14b is press-fitted with the same press-fitting allowance Δd as the liner having no extension cylinder portion 14b, the rigidity of the fitting cylinder portion 14a is increased, so that the deformation of the cylinder 5 is increased. End up.

  On the other hand, in the liner 14 of this embodiment, as shown in FIG. 4, a groove 14c in the length direction is formed on the outer peripheral side of the extension cylinder portion 14b. By doing in this way, the extension cylinder part 14b of the liner 14 partially has a thin part in the length direction, and the rigidity of the part decreases, so that the rigidity of the fitting cylinder part 14a is increased. Can be suppressed. Therefore, the deformation of the cylinder 5 due to the press-fitting of the liner 14 can be reduced, and the performance deterioration due to the input increase of the compressor can be suppressed.

  In the present embodiment, the groove 14c is formed in a cross direction having an angle of 90 degrees. However, the direction and the number of the grooves 14c are not limited to this, as long as at least one is formed. You can enjoy the effect. The cross-sectional shape of the groove 14c is not necessarily rectangular, and may be a groove shape having an R portion such as a semicircular shape. The groove 14c may be provided not on the outer peripheral side but on the inner peripheral side. The length of the groove 14c may be limited to a part of the extended cylinder portion 14b, but the effect of the present invention can be enjoyed better if it is provided over the entire length.

  In the present embodiment, the compression mechanism 102 is a rotary compression mechanism. As shown also in FIG. 2, in the rotary compression mechanism, the vane 32 partitions the cylinder chamber 15 into the suction chamber 25a and the discharge chamber 25b. It is formed close to the vane groove 34. Since the deformation of the cylinder 5 due to the press-fitting of the liner 14 appears toward the outside in the radial direction of the suction passage 19, the influence is large when the vane groove 34 is close, and the sliding loss of the vane 32 due to the deformation of the vane groove 34. There is a risk that the compressor performance will be reduced due to the increase of. Therefore, if the liner 14 of this embodiment is used, the rigidity increase of the fitting cylinder part 14a can be suppressed, which is effective.

Example 1
FIG. 5 shows the liner 14 in Example 1 of the present embodiment. In Example 1, the liner 14 is provided with a wavy convex portion 14d formed in a corrugated shape toward the radially outer side of the tube wall of the extended cylindrical portion 14b. The wavy convex portion 14d extends in the length direction of the liner 14, and has a property of elastically deforming like a spring against a load in the radial direction of the extension cylinder portion 14b. Therefore, compared to the case where the cross section of the extension cylinder portion 14b is circular and has the same wall thickness, the extension cylinder portion 14b is likely to be deformed in accordance with the deformation of the fitting cylinder portion 14a. It is possible to prevent the rigidity of the portion 14a from greatly increasing, and to suppress the deformation of the cylinder 5 due to the press-fitting of the liner 14, thereby preventing the compressor performance from being lowered.

  Note that the number, the arrangement angle, the shape, the length, and the like of the wavy convex portions 14d of the present embodiment are not limited to this as in the case of the above-described grooves 14c. A convex part may be provided over the perimeter of an outer periphery, and the R dimension of a waveform can be determined arbitrarily.

(Example 2)
FIG. 6 shows the liner 14 in Example 2 of the present embodiment. In the second embodiment, the liner 14 is formed such that the tube wall thickness of the extension cylinder part 14b is thinner than the fitting cylinder part 14a. By doing in this way, the rigidity of the extension cylinder part 14b becomes smaller than the fitting cylinder part 14a, and the raise of the rigidity of the fitting cylinder part 14a can be suppressed. Further, since the effect of the present invention can be enjoyed only by adjusting the thickness of the tube wall, a large processing cost is not required, and the manufacturing cost is reduced.

(Example 3)
FIG. 7 shows the liner 14 in Example 3 of the present embodiment. In the third embodiment, the liner 14 is made of a material whose extension cylinder part 14b is softer than the fitting cylinder part 14a, and the extension cylinder part 14b and the fitting cylinder part 14a are coupled by the respective claws 14g and 14h. By doing in this way, the rigidity of the extension cylinder part 14b can be made lower than the case where it is comprised with the same material as the fitting cylinder part 14a. For example, a resin such as PTFE or PET can be used as the material of the extension cylinder portion 14b. Moreover, it may not be couple | bonded with forms, such as a nail | claw 14g and 14h, for example, you may couple | bond with the adhesive agent etc.

(Embodiment 2)
8 is a cross-sectional view of a compressor according to a second embodiment of the present invention, FIG. 9 is a cross-sectional view taken along a cross-section CC of FIG. 8, and FIG. 10 is a cross-section DD of FIG. FIG. About the code | symbol in a figure, the same code | symbol is used about the component similar to Embodiment 1, and description is abbreviate | omitted.

  The compression mechanism 202 of the rotary compressor 200 according to the second embodiment is a so-called two-piston rotary compression mechanism provided with a compression block 203 in addition to the compression block 3 of the rotary compressor 100 of the first embodiment. The upper side of the compression block 203 and the lower side of the compression block 3 are closed by an intermediate plate 250. The lower part of the compression block 203 is closed by a lower bearing 207. A muffler 209 is disposed so as to cover the lower bearing 207.

  As shown in FIG. 9, the compression block 203 includes a cylinder 205, a piston 208, a vane 232, a suction passage 219, a discharge hole 240, and a spring 236.

  The shaft 204 includes a lower eccentric portion 204b in addition to the upper eccentric portion 204a. Both the upper eccentric part 204a and the lower eccentric part 204b discharge outward in the radial direction, but the eccentric part 204b is set to 180 deg with respect to the eccentric part 204a. The piston 8 of the compression block 3 is attached to the eccentric portion 204a. A piston 208 disposed inside the cylinder 205 is attached to the eccentric portion 204b.

  The suction passage 219 is formed in the cylinder 205. The suction passage 219 opens toward the cylinder chamber 215. The liner 14 is connected to the suction passage 219.

  Similar to the liner 14 of the first embodiment, the liner 14 shown in FIG. 10 has a fitting cylinder portion 14 a and an extension cylinder portion 14 b that are formed slightly larger than the inner diameter of the suction passage 219, and is press-fitted into the suction passage 219. ing. The liner 14 further has an extension cylinder part 14b formed continuously with the fitting cylinder part 14a. A groove 214c in the length direction (corresponding to the groove 14c in FIG. 4) is formed on the outer peripheral portion of the extension cylinder portion 14b. The cross-sectional shape of the groove 214c is rectangular, and is formed from the end of the extension cylinder part 14b to the vicinity of the boundary line with the fitting cylinder part 14a. Four grooves 214c are formed at an angle of 90 degrees on the outer periphery of the extension cylinder portion 14b.

  The refrigerant compressed by the compression block 203 is discharged to the lower side of the lower bearing 207 through a discharge hole (not shown) provided in the lower bearing 207. As shown in FIG. 8, the muffler 209 is attached to the lower part of the lower bearing 207 so that the refrigerant discharge space 251 is formed below the lower bearing 207. The compression mechanism 202 is formed with a communication hole for guiding the refrigerant from the refrigerant discharge space 251 to the refrigerant discharge space 51, and the refrigerant discharged from the compression block 203 passes through the communication hole and passes through the refrigerant discharge space 51. To the internal space 13 of the sealed container 1. The shaft 4 is rotatably supported by the upper bearing 6 and the lower bearing 207. Other configurations of the compressed block 203 are the same as those of the compressed block 3.

  In the two-piston rotary compression mechanism as in this embodiment, usually, two compression blocks are stacked with a closing member such as an intermediate plate interposed therebetween. A suction passage is formed in each of the cylinders constituting the upper and lower compression blocks, and a liner is press-fitted. Therefore, when a liner having an extended cylinder part is press-fitted, the upper and lower cylinders may be deformed by the fitting cylinder part having increased rigidity, and the upper and lower compression blocks may be affected by deformation. is there. That is, the influence on the compressor performance due to the deformation is greater than that of the one-piston rotary compressor.

  In this embodiment, the liner 14 of the present invention is applied to a two-piston rotary compression mechanism. As a result, deformation of the upper and lower cylinders 5 and 205 can be suppressed, so that the influence of deformation that should be larger than that in the case of the one-piston rotary type compression mechanism can be suppressed to prevent deterioration of the compressor performance. The configuration of the present invention is effective.

  INDUSTRIAL APPLICATION This invention is useful for the compressor of the refrigerating-cycle apparatus which can be utilized for electrical appliances, such as a water heater, a warm water heating apparatus, and an air conditioning apparatus.

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Motor 3, 203 Compression block 4, 204 Shaft 4a, 204a, 204b Eccentric part 5, 205 Cylinder 6 Upper bearing 7, 207 Lower bearing 8, 208 Piston 9,209 Muffler 9a Discharge hole 11 Discharge pipe 13 Internal space 14 Liner 14a Fitting cylinder part 14b Extension cylinder part 14c, 214c Groove 14d Wavy convex part 15, 215 Cylinder chamber 17 Stator 18 Rotor 19, 219 Suction passage 20 Suction port 21 Terminal 22 Oil reservoir 25a Suction chamber 25b Discharge chamber 32, 232 Vane 34 Vane groove 36, 236 Spring 40, 240 Discharge hole 43 Discharge valve 45 Seal region 51, 251 Refrigerant discharge space 61 Retention space 100, 200 Rotary compressor 102, 202 Compression mechanism 250 Middle plate

Claims (6)

An airtight container, and a compression mechanism disposed in the airtight container;
A suction passage formed in the compression mechanism and through which the refrigerant passes;
A liner press-fitted into the suction passage;
The liner
A fitting tube portion having an outer diameter formed slightly larger than the inner diameter of the suction passage;
An extension cylinder part formed continuously with the fitting cylinder part,
The compressor is characterized in that the extension cylinder part is configured to have lower radial rigidity than the fitting cylinder part. The portion including a thickness smaller than the thickness of the tube wall of the fitting tube portion is formed in a cross section perpendicular to the length direction of the liner of the tube wall of the extension tube portion. The compressor described in 1. The compressor according to claim 1, wherein a groove is formed in a length direction of the liner on a surface of a tube wall of the extension cylinder portion. 3. The compressor according to claim 1, further comprising a convex portion formed in a corrugated shape toward a radially outer side of a tube wall of the extension cylinder portion. 2. The compressor according to claim 1, wherein a tube wall thickness of the extension tube portion is formed thinner than a tube wall thickness of the fitting tube portion. The extension cylinder part is made of a material different from the fitting cylinder part, and the material constituting the extension cylinder part is softer than the material constituting the fitting cylinder part. The compressor described in 1.