JP5033391B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor, and more particularly to a rotary compressor suitable for use in an air conditioner having a refrigeration cycle.

  An example of a rotary compressor used in a refrigeration cycle is disclosed in Patent Document 1. In the rotary compressor described in this publication, an electric motor unit including a stator and a rotor is disposed in an upper portion of the hermetic case. A compression mechanism is disposed inside and below the sealed case. The rotor of the electric motor part is fixed to the shaft, and the shaft has an eccentric shaft part at the lower part. A roller of the compression mechanism portion is attached to the eccentric shaft portion of the shaft.

  In the compression mechanism portion, a substantially cylindrical cylinder is interposed between the main bearing and the sub-bearing arranged above and below. Five internal threads are formed in the cylinder at intervals in the circumferential direction. The main bearing is fastened to the female thread of the cylinder using five bolts. The auxiliary bearing is also fastened to the female thread of the cylinder using five bolts.

  An example of a conventional rotary compressor is described in Patent Document 2. In the rotary compressor described in this publication, in order to effectively prevent gas leakage from the cylinder, the rotary compression element configured in two stages closes the cylinder, the opening surface of the cylinder, and has a bearing for the rotary shaft. A support member, a discharge silencer chamber communicating with the inside of the cylinder, and a cover attached to the support member and closing the opening of the discharge silencer chamber. The cylinder, the support member, and the cover are fastened by a plurality of main bolts. The cylinder and the support member are fastened with an auxiliary bolt located outside the bolt.

JP-A-8-61276 JP 2003-97469 A

  In the rotary compressor, the gap between the outer surface of the roller and the inner surface of the cylinder is minimized when the rotation angle of the rotation shaft reaches a predetermined angle. For this reason, conventionally, after temporarily fastening the main bearing and the cylinder with a predetermined fastening force using a plurality of bolts, the main bearing is fixed with a jig or the like to adjust the position of the cylinder, and the rotation angle of the rotary shaft is It sets so that the said clearance gap may be achieved when it becomes a predetermined angle. When the positional relationship between the main bearing and the cylinder is adjusted, a plurality of bolts are further screwed and tightened with a predetermined torque.

  At that time, these operations are carried out using all of a plurality of bolts. As a result, it is necessary to fasten all the bolts in the temporary fastening and the final fastening, and much work time is required for the assembly work of the compressor unit. In Patent Document 1, it is described that five bolts are used. However, there is no description on how to use these bolts for fastening work, and consideration is given to reducing the assembly work time. Not.

Japanese Patent Application Laid-Open No. H10-228561 describes that the two types of bolts, a main bolt and an auxiliary bolt, are used to cope with a high-pressure CO ₂ refrigerant. However, in the rotary compressor described in Patent Document 2, a cover that is often made of a sheet metal or the like is fastened together with a cylinder and a support member for easy manufacture, so that variation due to dimensional variation and load is large. When fastening the cover, it is difficult to maintain the positional accuracy of the main bearing and the cylinder.

  The present invention has been made in view of the above problems of the prior art, and an object of the present invention is to facilitate assembly of compression elements in a hermetic rotary compressor. Another object is to reduce the time required to assemble the compression element. Still another object is to improve the positioning accuracy of the main bearing and the cylinder.

Feature of the present invention for achieving the above object, the electric motor at the top of the closed container, the rotary compressor of arranging the compression element driven by the electric motor at the bottom, the compression element is a rotating shaft, said rotating shaft a roller fitted in a cylinder disposed in the outer diameter side of the roller, a main bearing for clamping the cylinder up and down and the auxiliary bearing, and a fixing means for fixing the cylinder to said main bearing and said auxiliary bearing It has the fixing means, and five bolt holes formed on the circumference substantially equal pitch in the main bearing and the sub-bearing is formed in the cylinder, which is formed at a position corresponding to the bolt holes The main bearing and the cylinder using five female screws, three first bolt holes in the five bolt holes, and three first female screws in the five female screws Three first bolts for fastening Using the remaining two second bolt holes of the five bolt holes and the remaining two second female screws of the five female threads, two main screws are fastened to the main bearing and the cylinder. The first bolt hole is formed at the apex of an isosceles triangle having an acute angle, and the base of the isosceles triangle is a gap between the outer diameter surface of the roller and the inner diameter surface of the cylinder. Is parallel to the direction that minimizes the angle, and does not intersect the inner diameter surface of the cylinder .

And in this aspect, has a silencer cover covering the main bearings, wherein a second bolt hole with a second internal thread and said second bolt, tighten and wherein the silencer cover and the main bearing cylinder it may be of even you sintering.

Furthermore, the main bearing is formed, a third female screw used to attach the muffler cover to the main bearing, the rotary shaft within the triangle formed by said third internal thread and the second internal thread The center of the axis should be located.

  According to the present invention, since only three bolts are used when temporarily tightening the main bearing and the cylinder, the assembly operation of the hermetic rotary compressor is facilitated and the working time is shortened. Further, since the silencer cover is attached later to position the main bearing and the cylinder, the assembly accuracy of the main bearing and the cylinder is improved.

  Several embodiments of the rotary compressor according to the present invention will be described below with reference to the drawings. FIG. 1 is a longitudinal sectional view showing an embodiment of the rotary compressor 1. The rotary compressor 1 includes a sealed container 13 having a cylindrical body portion 22, a lid portion 12 that covers an upper portion of the body portion 22, and a bottom portion 21 that covers a lower portion of the body portion 22. An electric motor 14 having a stator 7 and a rotor 8 is disposed in the upper part of the sealed container 13. The rotor 8 of the electric motor 14 is fixed to the rotary shaft 2 extending vertically.

  An eccentric part 5 is formed at the lower part of the rotating shaft 2. The rotary shaft 2 is pivotally supported by the cylindrical portion of the main bearing 9 having a cylindrical portion and a flat plate portion, and the cylindrical portion of the auxiliary bearing 19 which also has a cylindrical portion and a flat plate portion. The main bearing 9 is fixed to the inner wall of the body portion 22 of the sealed container 13 by welding. The main bearing 9 supports components of the compression element 20 such as the cylinder 10 and the auxiliary bearing 19. Instead of the main bearing 9, a cylinder 10 to be described later can be fixed to the inner wall of the body portion 22 of the sealed container 13.

  The roller 11 of the compression element 20 is fitted to the eccentric portion 5 of the rotating shaft 2. A substantially cylindrical cylinder 10 is disposed between the flat plate portions of the main bearing 9 and the auxiliary bearing 19 so as to accommodate the cylindrical roller 11 therein. The roller 11, the cylinder 10, the main bearing 9, and the auxiliary bearing 19 constitute a compression element 20.

  A dome-shaped sound deadening cover 3 having a seating surface 17 formed on the outer diameter side is disposed on the opposite side of the flat plate portion of the main bearing 9 from the side facing the cylinder 10. The seating surfaces 17 of the silencer cover 3 are arranged at intervals in the circumferential direction, and each seating surface 17 is formed with a bolt through hole. An inner hole 23 through which the main bearing 9 passes is formed at the center of the sound deadening cover 3.

  The flat plate portion of the main bearing 9 and the flat plate portion of the sub-bearing 19 are formed with a plurality of bolt through holes at intervals in the circumferential direction, and the cylinder 10 is provided at a position corresponding to these bolt through holes. Screws 6a and 6b are formed. The bolt through holes in the seating surface 17 of the silencer cover 3 also correspond to the positions of the internal threads 6a and 6b of the cylinder 10. Since the bolt through holes and the female screws 6a and 6b are formed in this way, the silencer cover 3, the main bearing 9, the cylinder 10 and the auxiliary bearing 19 are stacked in order from the top and bottom, and fastened with the bolts 4, 4a and 4b. Thus, the compression element 20 is configured. The main bearing 9, the cylinder 10, and the auxiliary bearing 19 are formed by polishing or grinding a cast or iron-based sintered member.

  FIG. 2 shows a ZZ arrow view of FIG. That is, it is a top view of the cylinder 10 part. A space formed in the compression element 20 by the main bearing 9 and the sub bearing 19, the cylinder 10, and the roller 11 is a flat vane 18 to which pressing means such as a coil spring (not shown) is attached, and the compression space 31 and the suction space. It is divided into 32. The cylinder 10 is formed with a slot groove extending radially from the inner periphery to the outer diameter side, and the vane 18 is fitted in the slot groove.

  When the rotating shaft 2 rotates, the eccentric portion 5 of the rotating shaft 2 moves eccentrically, and the roller 11 rotates eccentrically according to the eccentric movement. Since the tip of the inner peripheral side of the vane 18 is pressed against the outer periphery of the roller 11 by the pressing means, the vane 18 moves in the slot groove of the cylinder 10 in the radial direction as the roller 11 rotates eccentrically.

  The setting of the position where the distance (gap) between the inner peripheral surface of the cylinder 10 and the outer peripheral surface of the roller 11 is minimized when the roller 11 is eccentrically rotated will be described below with reference to FIG. The center of the slot groove into which the vane 18 is fitted is taken as a reference axis. In FIG. 2, the Y axis is the reference axis. The axis of the rotary shaft 2 is such that the predetermined angle θ from the Y axis, the X axis rotated in this embodiment by the 270 ° rotary shaft, and the gap is the minimum gap δ, in this embodiment δ = 5 to 30 μm. The cylinder 10 is adjusted with respect to the center O in the X-axis direction.

  In the cylinder 10, a plurality of female screws 6 are formed at a radial position between the inner peripheral side and the outer peripheral side at intervals in the circumferential direction. In the present embodiment, five female screws 6 are formed on the circumference of a radius r centered on the point O at a constant pitch in the circumferential direction. The female screw 6 has a roundness of 2 mm (the radius is an error r, and up to r ± 2 mm is allowed), and the angle tolerance is ± 20 °.

  A reference female screw 6 is formed at a reference point P on the circumference of the radius r centered on the point O and 180 ° away from the reference axis. Two points Q and Q are selected on the circumference of the radius r centered on the point O and symmetrically with respect to the Y axis which is the reference axis, and the female thread 6 is formed. Two points Q and Q are on the vane 18 side. The triangle formed by the three points Q, P, and Q is an isosceles triangle, and the apex angle QPQ is an acute angle of about 36 degrees. With respect to the line segment QQ, ± 15 ° is an allowable range of deviation from parallel with respect to the direction of the angle θ that is the adjustment direction of the cylinder 10. Thus, even if the line segment QQ is shifted, the point O is located inside the triangle QPQ.

The three female screws 6 formed at the points P, Q, and Q are called first female screws 6a. The female screw 6 positioned between the point P and the point Q is referred to as a second female screw 6b. Each female screw 6 penetrates in the height direction of the cylinder 10 and can be bolted from both upper and lower sides of the cylinder 10. Further, five through-holes 16 were provided in the main bearing 9 and the sub-bearing 19 corresponding to the circumferential direction and radial position of each of the female screws 6a and 6b. A flat seat surface 17 having a through hole 16b was provided only at a position corresponding to the second female screw 6b of the silencer cover 3. The number of seating surfaces 17 is two.

  The operation of the rotary compressor 1 configured as described above will be described below. In the compression element 20, the eccentric part 5 of the rotating shaft 4 rotates eccentrically, and the roller 11 moves eccentrically. The gas refrigerant, which is a working fluid, is sucked into the compression element 20 from the suction port 25 and compressed from a low pressure to a high pressure. The gas refrigerant in the compression element 20 is discharged into the muffler cover 3 through a discharge valve (not shown) that opens when the pressure reaches a preset pressure. The discharged gas refrigerant enters the sealed container 13 through a gap between the main bearing 9 and the inner hole 23 formed in the center portion of the sound-absorbing cover 3 and a discharge hole 24 formed in a part of the dome portion of the sound-absorbing cover 3. Discharged. The gas refrigerant discharged into the hermetic container 13 is discharged to the outside of the rotary compressor 1 from the discharge pipe 27 provided in the lid portion 12.

The assembly procedure of 20 compression elements will be described with reference to FIG. In FIG. 3, the top and bottom of FIG. 2 are reversed. That is, the rotating shaft 2 is upside down. The roller 11 is fitted to the eccentric portion 5 of the rotating shaft 2. The rotary shaft 2 fitted with the roller 11 is inserted into the cylindrical portion of the main bearing 9 from the axial direction. The side surface of the roller 11 contacts the flat plate portion of the main bearing 9, and the rotary shaft 2 is held by the main bearing 9. The cylinder 10 is lowered from above along the axis of the rotary shaft 2 and brought into contact with the flat plate portion of the main bearing 9.

  In this state, the three first bolts 4a are screwed into the first female screw 6a from the lower side. At that time, the main bearing 9 and the cylinder 10 are temporarily tightened by screwing with a predetermined fastening force or a predetermined torque. The temporarily tightened main bearing 9 and cylinder 10 are fixed and held using a jig. At that time, the position of the cylinder 10 is moved in the direction shown in FIGS. 2 and 3 and adjusted to a predetermined position. When the position of the cylinder 10 is positioned at a predetermined position, the first bolt 4a is screwed with the second predetermined tightening force or the second predetermined torque and finally tightened.

  Next, the auxiliary bearing 19 is inserted into the rotating shaft 2 along the axis of the rotating shaft 2. Five bolts 4 are formed on the cylinder 10 from above and screwed into the screws 6a and 6b, and finally tightened with a predetermined fastening force. As a result, the positions of the main bearing 9, the cylinder 10 and the auxiliary bearing 19 having the sliding portions are fixed. Thereafter, the silencer cover 3 is inserted into the cylindrical portion of the main bearing 9 from below using the inner hole 23 as a guide. A counterbore surface is formed on the back side of the flat plate portion of the main bearing 9, and the silencer cover 3 is brought into contact with the counterbore surface. The two second bolts 4b are screwed into the second female screw 6b with a predetermined fastening force, and the sound deadening cover 3 and the cylinder 10 are finally tightened.

  FIG. 4 shows an arrow A view when assembling the compression element 20 shown in FIG. 3, and FIG. 5 shows an arrow B view. A first bolt 4 a is arranged inside the dome shape of the sound deadening cover 3. Two seating surfaces 17 to which the second bolts 4b can be attached are arranged outside the dome shape. The silencer cover 3 is manufactured by integrally molding an iron-based plate material having a thickness of 1 to 3 mm by press working. On the outer diameter side of the main bearing 9, air holes 26 that are long in the circumferential direction are formed at approximately three regular pitches in the circumferential direction. The muffler cover 3 is cantilevered by two second bolts 4b with respect to an axis XX passing through the point O.

  According to the present embodiment, since only the three first bolts 4a are used for positioning the main bearing 9 and the cylinder 10, the number of temporary fastenings is reduced and the working time is shortened. Further, since the first female screw 6a is disposed at two positions symmetrical to the reference line and on the reference position side opposite to the reference line, the fastening force by temporary tightening can be made uniform with only the first bolt 4a. As a result, when the cylinder 10 is positioned, it can be adjusted with a predetermined lateral load without applying an excessive force, and the assemblability is improved. Further, the assembly accuracy is improved. Further, since the silencer cover 3 having a large dimensional variation and easily deformed because of a press-processed product is attached after positioning the main bearing 9, the cylinder 10, and the auxiliary bearing 19, the positioning accuracy of the main bearing 9 and the cylinder 10 is improved. .

  Another embodiment of the rotary compressor according to the present invention will be described with reference to the top view of the cylinder 10 in FIG. 6 corresponds to FIG. 2 of the embodiment shown in FIG. This embodiment is different from the embodiment shown in FIG. 2 in that the position of the reference point P forming the reference female screw 6 is brought close to the reference axis on which the slot groove into which the vane 18 is fitted is formed. One of the points Q serving as the first female screw 6a is arranged at a position 180 ° away from the reference axis. The relative positions of the first and second female screws 6a and 6b are the same as those in the embodiment shown in FIG.

  It is necessary to change the angle at which the gas refrigerant is discharged in accordance with the set discharge conditions of the compression element 20. The discharge space 31 is enlarged under low pressure conditions, and the discharge space 31 is reduced under high pressure conditions. This example is a case of a low pressure condition as compared with the example shown in FIG. The rotation angle θ from the reference axis of the rotary shaft 2 that becomes the minimum clearance δ is 225 °.

  Also in the present embodiment, the fastening force of the temporary fastening by the first bolt 4a can be made uniform with respect to the adjustment direction of the cylinder 10, and the position of the cylinder 10 can be adjusted with a constant lateral load. Therefore, the assembling property is improved and the assembling accuracy is also improved. As described above, even if the rotation angle θ that is the minimum clearance is changed, the assembling property and the assembling accuracy are not deteriorated, and it is possible to cope with both the low pressure condition and the high pressure condition.

  Still another embodiment of the rotary compressor according to the present invention will be described with reference to a longitudinal sectional view of 20 parts of the compression element shown in FIG. 7 and FIG. The present embodiment differs from the embodiment shown in FIG. 1 in that, in addition to the two second female screws 6b formed in the cylinder 10, a third female screw 27 is attached to the main bearing 9 for mounting the noise-reducing cover 3. The flat plate portion is formed. The positions where the first and second female screws 6a and 6b are formed are the same as those in the embodiment shown in FIG.

  Since the 3rd female screw 27 is only what attaches the sound deadening cover 3, any position may be sufficient if it does not interfere with the 1st bolt 4a screwed to the 1st female screw 6a. A third bolt 28 is screwed to the third female screw 27. Note that one seating surface 17 is added to the silencer cover 3, and the third bolt 28 is fastened at the same assembly stage as the second bolt 4b. The nominal diameter of the female screw 27 was the same as that of the female screw 6 so as not to deteriorate the workability. In this embodiment, a through screw is used as the female screw 27, but a dead screw may be used.

  The third bolt 28 and the third female screw 27 may be anywhere as long as they do not interfere with the other bolts 4a and 4b, but are arranged on the same circumference as the other female screws 4a and 4b in consideration of ease of manufacture. . When the position of the second bolt 4b is a point S and the position of the third bolt 28 is a point R, the triangle SRS is set to an approximately isosceles triangle having the angle SRS as an apex angle. At this time, the rotation center O is located inside the triangle SRS. In addition, it is desirable to remove the positions of the female screw 27 and the third bolt 28 from the sliding range of the vane 18.

  In the present embodiment, since the silencer cover 3 is supported at both ends with respect to the axis XX, even when the silencer cover 3 has low rigidity, deformation due to pressure fluctuations accompanying discharge of the gas refrigerant from the cylinder 10 can be suppressed. . Furthermore, according to the present embodiment, no extra processing is required other than the main bearing 9 and the muffler cover 3, and the above effects can be obtained while suppressing an increase in processing cost.

  Still another embodiment of the rotary compressor according to the present invention will be described with reference to FIGS. The rotary compressor 1 of the present embodiment is a two-stage compressor having two compression elements 20A and 20B. FIG. 9 is a longitudinal sectional view of the two-stage rotary compressor 13b. Two eccentric portions 5A and 5B are formed on the rotating shaft 2 to which the rotor 8 of the electric motor 14 is attached. The eccentric portions 5A and 5B are 180 degrees out of phase with each other. As in the case of the single-stage compressor, the rotary shaft 2 is pivotally supported by the cylindrical portion of the main bearing 9 and the cylindrical portion of the auxiliary bearing 19.

  The roller 11A attached to the upper eccentric portion 5A and the cylinder 10A arranged so as to accommodate the roller 11A are arranged on the upper and lower sides in the axial direction by the flat plate portion of the main bearing 9 and the partition plate 15. Retained. The roller 11B attached to the lower eccentric portion 5B and the cylinder 10B arranged so as to accommodate the roller 11B are arranged in the axial direction on the upper and lower side surfaces of the partition plate 15 and the sub-bearing 19 in the axial direction. Retained.

The partition plate 15 is made of a substantially disc-shaped casting or an iron-based sintered member. The partition plate 15 is formed with five inner holes 30 for allowing the eccentric portion 5B of the rotating shaft 2 to pass therethrough and five through holes 16 for allowing the bolts 4 to pass. A dome-shaped second silencing cover 3 </ b> B is attached to the lower portion of the auxiliary bearing 19 so as to cover the auxiliary bearing 19. An inner hole 23B is formed in close contact with the sub bearing 19 at the center of the second silencing cover 3B. Others are the same as those of the single cylinder rotary compressor 1 shown in FIG. The partition plate 15 is a substantially disk-shaped casting or an iron-based sintered member. The partition plate 15 is formed with five inner holes 30 through which the eccentric portion 5B passes during assembly and five through holes 16 through which the bolts 4 pass.

  In the rotary compressor 1b of the present embodiment configured as described above, the gas refrigerant that is the working fluid is sucked from the suction ports 25A and 25B of the cylinders 10A and 10B, and the rollers 11A and 11B rotate eccentrically, so that the pressure is reduced from low to high. Until compressed. The gas refrigerant of each compression element 20A, 20B is discharged into the first silencing cover 3 and the second silencing cover 3B through a discharge valve (not shown) that opens when a preset pressure is reached.

  The gas refrigerant discharged into the second silencer cover 3B is discharged to the first silencer cover 3 through the auxiliary bearing 19 and the communication hole 31 formed in the cylinder 10B, the partition plate 15, the cylinder 10A, and the main bearing 9. . The gas refrigerant in the first silencer cover 3 is discharged into the sealed container 13 through the gap between the inner hole 23 of the first silencer cover 3 and the main bearing 9 and the discharge hole 24 of the first silencer cover 3. The gas refrigerant discharged into the hermetic container 13 is discharged out of the rotary compressor 1b from a discharge pipe 27 provided in the lid portion 12.

In FIG. 10, the 2nd compression element 20B is shown by the ZA-ZA arrow line view of FIG. The first compression element 20A is the same as that shown in FIG. 2 except that the communication hole 31 is provided in the cylinder 10A, and the illustration thereof is omitted. The cylinder 10 </ b> B of the second compression element 20 </ b> B was formed with five through holes 16 through which the bolts 4 penetrate at the positions of the screws 6 to form the cylinder 10 </ b> A of the first compression element 20 </ b> A. A communication hole 31 was formed at a position where it did not interfere with the through hole 16. The diameter and position of the communication hole 31 are the same in the auxiliary bearing 19, the partition plate 15, the cylinder 10 </ b> A, and the main bearing 9.

  Similarly to the first silencing cover 3, the second silencing cover 3B was manufactured by integrally molding an iron-based plate material having a thickness of 1 to 3 mm by pressing. The shape of the second silencing cover 3B is substantially the same as that of the first silencing cover 3, but an inner hole 23B that is in close contact with the auxiliary bearing 19 is formed without forming a discharge hole in the dome portion.

A method for assembling the compression elements 20A and 20B of the rotary compressor 1b shown in this embodiment will be described below with reference to FIG. In FIG. 11 as well, as in the embodiment shown in FIG. The roller 11 </ b> A is fitted into the eccentric portion 5 </ b> A of the rotating shaft 2. The rotating shaft 2b to which the roller 11A is attached is inserted into the cylindrical portion of the main bearing 9, and the roller 11A is brought into contact with the flat plate portion of the main bearing 9.

  In this state, the cylinder 10A is lowered from above along the rotary shaft 2b and brought into contact with the flat plate portion of the main bearing 9. The three first bolts 4a are screwed into the first female screw 6a from the back side of the main bearing 9, and the main bearing 9 and the cylinder 10A are temporarily tightened with a predetermined fastening force. The main bearing 9 is fixed with a jig or the like, and the cylinder 10A is adjusted by moving horizontally in the direction indicated by the arrow in FIG. After positioning the cylinder 10A, the first bolt 4a is further screwed and tightened.

  Next, the inner hole 30 of the partition plate 15 is passed along the eccentric portion 5B of the rotating shaft 2b, and the partition plate 15 is brought into contact with the upper surface of the cylinder 10A. The roller 11B is fitted to the eccentric part 5B of the rotating shaft 2b. The cylinder 10B is lowered along the rotation shaft 2b and brought into contact with the upper surface of the partition plate 15. The auxiliary bearing 19 is lowered along the rotating shaft 2b so that the rotating shaft 2b passes through the cylindrical portion of the auxiliary bearing 19. Using the three first bolts 4a, the auxiliary bearing 19 and the upper cylinder 10B and the partition plate 15 are screwed into the first female screw 6a of the lower cylinder 10A and temporarily tightened with a predetermined fastening force. .

  Since the upper cylinder 10B is in a temporarily tightened state, the cylinder 10B is moved in the horizontal direction indicated by an arrow in FIG. 11 to adjust the position of the cylinder 10B. At this time, the minimum gap position formed by the cylinder 10B is set on the same side as the minimum gap position formed by the cylinder 10A. After positioning the cylinder 10B, the first bolt 4a is further screwed and tightened.

  When the arrangement of the main bearing 9 and the cylinder 10 having the sliding portion, the partition plate 15, and the auxiliary bearing 19 is fixed, the silencer cover 3 arranged on the lower side is connected to the lower cylinder 10A with the main bearing 9 interposed therebetween. Screw into the second female screw 6b using the second bolt 4b. At that time, the second bolt is tightened from the back side of the main bearing 9 with a predetermined fastening force. The second silencing cover 3B is disposed on the upper surface of the auxiliary bearing 19, and the second silencing cover 3B is screwed into the lower cylinder A and the second female screw 6b using two second bolts 4b.

  According to this embodiment, since the main bearing 9 and the cylinder 10A are positioned by only the three first bolts 4a in the two-cylinder rotary compressor 1, the number of times of temporary tightening of the lower cylinder 10 is reduced. Work time is shortened. Similarly, since the auxiliary bearing 19 and the cylinder 10B are positioned using only the three first bolts 4a, the time required for positioning the upper cylinder is also shortened.

  According to the present embodiment, since the first female screw 6a is arranged at the apex of an isosceles triangle having an acute apex angle, even if it is temporarily tightened using only the first bolt 4a, the fastening force is equalized during the temporary tightening. Is done. As a result, the positions of both the upper cylinder 10A and the lower cylinder 10B can be adjusted with a predetermined lateral load, and the assemblability of the rotary compressor is improved. Further, the rotary compressor can be assembled with high accuracy.

  According to the present embodiment, since it is necessary to form a dome shape, the main bearing 9 and the cylinders 10A, 10A, Since the silencer covers 3 and 3B are attached to the compression elements 20A and 20B after positioning the partition plate 15, the cylinder 10B, and the auxiliary bearing 19, the relative positions of the main bearing 9 and the cylinder 10A, the cylinder 10B, and the auxiliary bearing 19 are accurately determined. Can be positioned.

  A modification of the embodiment shown in FIG. 11 will be described with reference to FIG. In the embodiment shown in FIG. 11, the first and second female screws 6a and 6b are formed in the cylinder 10A located on the lower side during assembly. However, in this modification, the first and second female screws 6a and 6b are assembled. It is sometimes provided in the cylinder 10B located on the upper side. In the rotary compressor 1b, since the main bearing 9 is welded to the body portion 22 of the hermetic container 13, thermal deformation accompanying welding occurs. According to the present embodiment, since the bolt 4 is fastened to the cylinder 10B farther away from the main bearing 9, welding deformation and tightening deformation can be dispersed. That is, the effects of welding deformation and tightening deformation can be suppressed without degrading the assembly workability as compared with the embodiment shown in FIG.

The longitudinal cross-sectional view of one Example of the rotary compressor which concerns on this invention. The top view of the compression element which the rotary compressor shown in FIG. 1 has. The figure explaining the assembly method of the compression element which the rotary compressor shown in FIG. 1 has. FIG. B arrow view in FIG. The top view of the other Example of the compression element which the rotary compressor shown in FIG. 1 has. The longitudinal cross-sectional view of the further another Example of the compression element which the rotary compressor shown in FIG. 1 has. C arrow line view in FIG. The longitudinal cross-sectional view of the other Example of the rotary compressor which concerns on this invention. The ZA-ZA arrow directional view of FIG. The figure explaining the assembly method of the compression element which the rotary compressor shown in FIG. 9 has. The figure explaining the other assembly method of the compression element which the rotary compressor shown in FIG. 9 has.

Explanation of symbols

1, 1a Compressor 2, 2b Rotating shaft 3, 3B Silent cover 4, 4a, 4b Bolt 5, 5A, 5B Eccentric part 6, 6a, 6b Female thread 9 Main bearing 10, 10A, 10B Cylinder 11, 11A, 11B Roller 15 Partition plate 16 Through-hole 19 Sub bearing 20, 20A, 20B Compression element

Claims (3)

In a rotary compressor in which an electric motor is arranged at the upper part of the hermetic container and a compression element driven by this electric motor is arranged at the lower part,
Said compression element and the rotating shaft, a roller fitted to said rotary shaft, a cylinder disposed on the outer diameter side of the roller, a main bearing for clamping the cylinder up and down and the auxiliary bearing, the main bearing of the cylinder And fixing means for fixing to the auxiliary bearing,
The fixing means includes
And five bolt holes formed on the circumference substantially equal pitch in the main bearing and the sub-bearing,
Five female screws formed in the cylinder and at positions corresponding to the bolt holes ;
Three first bolt holes in the five bolt holes and three first female threads in the five female threads are used to fasten the main bearing and the cylinder. The first bolt;
Using the remaining two second bolt holes of the five bolt holes and the remaining two second female screws of the five female threads, two bolts for fastening the main bearing and the cylinder are fastened. Including a second bolt,
The first bolt hole is formed at the apex of an isosceles triangle having an acute angle.
The rotary compressor characterized in that the base of the isosceles triangle is parallel to a direction that minimizes a gap between the outer diameter surface of the roller and the inner diameter surface of the cylinder, and does not intersect the inner diameter surface of the cylinder . A silencer cover covering the main bearing,
Wherein a second bolt hole with a second internal thread and said second bolt, rotary as claimed in claim 1, wherein the silencer cover and the main bearing and the cylinder and the concluded to Turkey Compressor. Said main bearing is formed, a third female screw used to attach the muffler cover to the main bearing,
3. The rotary compressor according to claim 2, wherein an axis of the rotary shaft is located within a triangle formed by the second female screw and the third female screw.

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