JP6548915B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor that is applied to an air conditioner or the like and that compresses and discharges a refrigerant.

  In a compressor used for an air conditioner or the like, a compressor is driven by an electromagnetic motor. The electromagnetic motor includes a rotor, a stator, and the like, and the rotor and the compression unit are connected to each other via a drive shaft. The compressor rotates as the motor rotor rotates.

  The compression unit includes, for example, a rotary compression mechanism, and the rotary compression mechanism includes a cylinder body, an upper bearing and a lower bearing that support a rotating shaft, and the like. The refrigerant drawn into the cylinder chamber formed in the cylinder body is compressed by the rotation of the roller in the cylinder chamber, and then discharged into the muffler (discharge chamber) through the discharge hole and the discharge valve. Thereafter, the refrigerant discharged into the muffler is sent to the motor side in the hermetic container (housing) of the compressor.

  The muffler is, for example, substantially wedge-shaped and attached to the upper bearing so as to cover the discharge valve, as described in Patent Document 1 below. Patent Document 1 discloses that a rib is integrally formed on an upper bearing, which is a frame, to improve the rigidity of the frame.

Patent No. 3301837

  In the above-mentioned rotary type compression mechanism, since the refrigerant discharged into the muffler is compressed in the cylinder chamber to have a high temperature, the refrigerant such as the muffler and the upper bearing are heated during operation. As a result, the relatively low temperature refrigerant drawn into the cylinder chamber is heated by the upper bearing or the like. Therefore, since the rotary compression mechanism sucks in and compresses the refrigerant whose temperature has risen, the efficiency is deteriorated.

  Further, unlike Patent Document 1, in the upper bearing in which the rib is not formed, since the rigidity is weak, for example, resonance occurs at a characteristic value (about 1 kHz) of the low frequency region of the upper bearing. As a result, there is a problem that the bearing and the drive shaft (shaft) are elastically deformed and the noise increases.

  This invention is made in view of such a situation, Comprising: It aims at providing the compressor which can improve the rigidity of a bearing and can reduce the heat transfer to a cylinder main body.

In order to solve the above-mentioned subject, a compressor of the present invention adopts the following means.
That is, in the compressor according to the present invention, a cylinder body of a rotary type compression mechanism, a bearing provided on one surface side of the cylinder body and supporting a drive shaft, and a plate portion installed on one surface side of the bearing The bearing is provided upright from the one surface of the bearing and has a wall formed along the radial direction of the bearing, surrounded by the wall and the plate, and discharged from the cylinder body And a heat insulating portion which is separated from the refrigerant circulating portion by the wall portion and the plate portion while being surrounded by the wall portion and the plate portion, and a heat insulating portion which the refrigerant does not circulate is formed. The bearing has a recess formed by the outer peripheral wall of the bearing, the central wall of the bearing, and the wall portion, and the heat insulating portion is a space surrounded by the recess and the plate portion. The bearing is disposed in the heat insulating portion, Is erected from said one side of the serial bearing further comprises a first rib formed along a radial direction of the bearing.

According to this configuration, the heat insulating portion, through which the refrigerant does not flow, is formed separately from the refrigerant flowing portion through which the refrigerant flows, and the heat insulating portion is a wall formed along the radial direction of the bearing and one surface of the bearing It is separated from the refrigerant circulation part by the plate part installed in the side. As a result, the heat insulating portion becomes a heat insulating space in which the heat of the refrigerant is hard to be transmitted, and the temperature rise of the cylinder body can be reduced, and the temperature rise of the refrigerant flowing on the suction side of the cylinder body can be reduced. The refrigerant flow portion receives the refrigerant discharged from the cylinder body, and exerts the muffling effect.
Also, since the wall is erected from one surface of the bearing and formed along the radial direction of the bearing, the rigidity of the bearing is enhanced.
In addition, in order to divide a refrigerant | coolant distribution part and a heat insulation part, a wall part is extended in two different directions from the center of a bearing, for example. The angle between the two wall portions and the angle between the wall portion and the first rib is preferably less than 180 °. Thereby, the rigidity of the bearing can be further enhanced.
Further, not only the wall but also the first rib is formed on one surface of the bearing along the radial direction of the bearing. Therefore, the rigidity of the bearing can be enhanced.

  In the above invention, at least two cylinder bodies are provided, and the bearing is erected from the one surface of the bearing in the refrigerant flow portion, and further includes a second rib formed along the radial direction of the bearing. The refrigerant circulating unit is separated into at least two separated spaces by the second rib, and the one separated space discharges the refrigerant from one of the cylinder bodies, and the other separated spaces The refrigerant is discharged from the cylinder body.

  According to this structure, the refrigerant | coolant distribution part which a refrigerant | coolant distribute | circulates is divided into two isolation | separation space by a 2nd rib. Then, the refrigerant discharged from one cylinder body flows in one separation space, and the refrigerant discharged from the other cylinder body flows in the other separation space. Therefore, the refrigerant discharged from one cylinder main body and the other cylinder main body both circulate through the separation space of the refrigerant circulation part and are muffled.

  In the above invention, in at least two of the separation spaces, the refrigerant can flow from one side to the other, and in the plate portion, only one discharge hole through which the refrigerant is discharged from the separation space is formed.

  According to this configuration, the refrigerant supplied from the one cylinder main body and the refrigerant supplied from the other cylinder main body are merged in the separation space of the refrigerant circulating portion, and the merged refrigerant is formed in the plate portion The ink is discharged from the separation space only through the discharge holes of As a result, when one cylinder body and another cylinder body are provided, it is not necessary to separately provide a member for joining the refrigerant outside the compression mechanism.

  In the above-mentioned invention, the second rib is formed with a notch which is partially cut away in the radial direction of the bearing so that the refrigerant can flow from one side to the other in at least two of the separated spaces.

  According to this configuration, since the refrigerant flows through the notch portion of the second rib, the height of the second rib is not reduced except at the notch portion, and the space between the at least two separation spaces does not decrease. The refrigerant flows. Therefore, the rigidity can be enhanced as compared with the case where the heights of the second ribs are all lowered along the radial direction of the bearing in order to cause the refrigerant to flow from one to the other in the separation space.

  In the above invention, groove portions are formed in the plate portion at positions corresponding to the second ribs such that the refrigerant can flow from one side to the other in at least two of the separation spaces.

  According to this configuration, since the refrigerant flows through the groove portion formed in the plate portion, the refrigerant flows between at least two separation spaces without reducing the height of the second rib. Therefore, in the case where the heights of the second ribs are all lowered along the radial direction of the bearing in order to cause the refrigerant to flow from one to the other in the separation space, or when the notch is formed in part of the second ribs Compared with, the rigidity can be enhanced.

  According to the present invention, the rigidity of the bearing can be enhanced by the wall portion, and the heat transfer to the cylinder body can be reduced, so that the temperature rise of the cylinder body can be reduced and the refrigerant flowing on the suction side of the cylinder body The temperature rise can be reduced.

It is a longitudinal section showing a compressor concerning a 1st embodiment of the present invention. It is a cross-sectional view which shows the cylinder main body of the compressor which concerns on 1st Embodiment of this invention. It is a top view showing the upper bearing and muffler board of the compressor concerning a 1st embodiment of the present invention. It is a top view showing the upper bearing of the compressor concerning a 1st embodiment of the present invention. FIG. 5 is a longitudinal cross-sectional view cut along the line VV of FIG. 3; FIG. 5 is a longitudinal sectional view cut along the line VI-VI in FIG. 4; It is a schematic longitudinal cross-sectional view which shows the upper bearing and muffler plate of a compressor concerning a 1st embodiment of the present invention. It is a top view showing the upper bearing and muffler board of the compressor concerning a 2nd embodiment of the present invention. It is a top view showing the upper bearing of the compressor concerning a 2nd embodiment of the present invention. It is a schematic longitudinal cross-sectional view which shows the upper bearing and muffler plate of the compressor concerning 2nd Embodiment of this invention. It is a schematic longitudinal cross-sectional view which shows the upper bearing and muffler plate of the compressor concerning the 1st modification of a 2nd embodiment of the present invention. It is a schematic longitudinal cross-sectional view which shows the upper bearing and muffler plate of the compressor concerning the 2nd modification of a 2nd embodiment of the present invention. It is a schematic longitudinal cross-sectional view which shows the upper bearing and muffler plate of the compressor concerning the 3rd modification of a 2nd embodiment of the present invention. It is a top view showing the upper bearing and muffler board of the compressor concerning the 4th modification of a 2nd embodiment of the present invention.

First Embodiment
Hereinafter, a compressor 1 according to a first embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1, the multi-cylinder rotary compressor 1 according to the present embodiment includes a cylindrical hermetic container 2 whose upper and lower portions are sealed by an upper cover 3 and a lower cover 4, and the upper side of the inside A motor 5 is installed at the site, and a rotary type compression mechanism 6 driven by the motor 5 is installed at the lower site.

  A mounting leg 7 is provided on the lower periphery of the closed container 2. Moreover, the discharge piping 8 which penetrates the upper cover 3 is provided in the upper part of the airtight container 2, and the discharge piping 8 makes high-pressure refrigerant gas compressed with the multi-cylinder rotary type compressor 1 to the refrigerating cycle side. Exhale. Furthermore, an accumulator 9 is attached to the outer peripheral portion of the closed container 2. The accumulator 9 separates liquid components such as oil and liquid refrigerant contained in low-pressure refrigerant gas returning from the refrigeration cycle side, Only a minute is sucked into the compression mechanism 6 through the suction pipes 10 and 11.

  The motor 5 includes a stator 12 and a rotor 13. The stator 12 is fixed to the inner peripheral surface of the sealed container 2 by press fitting or the like. The rotor 13 can transmit the rotational drive force of the rotor 13 to the compression mechanism 6 through the drive shaft 14 by the drive shaft 14 being coupled and integrated. Further, at the lower portion of the drive shaft 14, a first eccentric pin 15 and a second eccentric pin 16 are provided corresponding to a first roller 24 and a second roller 25 of the rotary type compression mechanism 6 described later.

  The rotary compression mechanism 6 is a two-cylinder type in the present embodiment, and the first and second compression mechanisms 6A and 6B have a first cylinder chamber 17 and a second cylinder chamber 18 formed therein. The compression mechanism 6 further includes a first cylinder body 19 and a second cylinder body 20, a partition plate (separator plate) 21, an upper bearing 22, a lower bearing 23, and the like.

  The first cylinder body 19 and the second cylinder body 20 are fixedly installed in the sealed container 2 in correspondence with the first eccentric pin 15 and the second eccentric pin 16 of the drive shaft 14. The partition plate 21 is interposed between the first cylinder main body 19 and the second cylinder main body 20, and divides the first cylinder chamber 17 and the second cylinder chamber 18. The upper bearing 22 is provided on the upper surface of the first cylinder main body 19 to define the first cylinder chamber 17 and to support the drive shaft 14. The lower bearing 23 is provided on the lower surface of the second cylinder main body 20 and defines the second cylinder chamber 18 and supports the drive shaft 14.

  The first and second compression mechanisms 6A and 6B respectively include a first roller 24 and a second roller 25 and blades 28 and 29.

  The first roller 24 and the second roller 25 are rotatably fitted to the first eccentric pin 15 and the second eccentric pin 16, respectively, and rotate in the first cylinder chamber 17 and the second cylinder chamber 18. The first eccentric pin 15 and the second eccentric pin 16 are coupled to the drive shaft 14 and integrally rotate with the drive shaft 14. The center of gravity of the second roller 25 fitted to the second eccentric pin 16 is located opposite to the center of gravity of the first roller 24 fitted to the first eccentric pin 15 with respect to the axis of the drive shaft 14.

  The blades 28 and 29 are slidably fitted in blade grooves 26 and 27 provided in the first cylinder body 19 and the second cylinder body 20, as shown in FIG. 2) Divide the inside of the cylinder chamber 18 into the suction chamber side and the discharge chamber side.

  Low pressure refrigerant gas is drawn into the first cylinder chamber 17 and the second cylinder chamber 18 of the first and second compression mechanisms 6A and 6B from the suction pipes 10 and 11 through the suction ports 30 and 31, respectively.

  The refrigerant gas drawn into the first cylinder chamber 17 is compressed by the rotation of the first roller 24, and then, through the discharge hole and the discharge valve (not shown), the refrigerant flow portion 38 of the upper bearing 22 described later. And then discharged into the muffler 32. The muffler 32 is, for example, substantially wedge-shaped and attached to the upper bearing 22 so as to cover the discharge hole and the discharge valve (not shown). The refrigerant gas drawn into the second cylinder chamber 18 is compressed by the rotation of the second roller 25, and then discharged into the muffler 32 through the discharge hole and the discharge valve. The refrigerant gas discharged into the muffler 32 is discharged into the closed container 2 and then sent out to the refrigeration cycle through the discharge pipe 8.

  The first cylinder body 19 and the second cylinder body 20 constituting the compression mechanism 6, the partition plate 21, the upper bearing 22 and the lower bearing 23 are integrally fastened and fixed via bolts. Further, the bottom of the closed container 2 is filled with refrigeration oil 34 such as PAG oil or POE oil, and the lubrication portion in the compression mechanism 6 is provided through the oil supply hole or the like provided in the drive shaft 14 Refueling is possible. An appropriate amount of extreme pressure agent adapted to each oil is added to the refrigerator oil 34. In addition, the oil supply mechanism to the compression mechanism 6 is a structure used normally, and abbreviate | omits detailed description here.

  The first balance weight 35 is provided on the upper surface of the rotor 13, that is, on one side of the drive shaft 14 in the axial direction and opposite to the side on which the compression mechanism 6 is located. Further, the center of gravity of the first balance weight 35 is located on the opposite side of the center of gravity of the first roller 24 with respect to the axis of the drive shaft 14. The second balance weight 36 is provided on the lower surface of the rotor 13, that is, on the other side of the drive shaft 14 in the axial direction and on the side where the compression mechanism 6 is located. Further, the center of gravity of the second balance weight 36 is located on the opposite side of the center of gravity of the second roller 25 with respect to the axis of the drive shaft 14.

  By providing the first balance weight 35 and the second balance weight 36 on the upper surface and the lower surface of the rotor 13, the centrifugal force applied to the first balance weight 35 and the second balance weight 36 is obtained by the first roller 24 and the second roller 25. And the centrifugal force exerted on the first roller 24 and the second roller 25 caused by the rotation of

  In the rotor 13, a plurality of steel plates are mutually insulated and stacked in the axial direction of the drive shaft 14. The steel plate is an example of a magnetic metal plate, and may be another magnetic metal plate. By laminating the steel plates, generation of eddy current is suppressed. Each steel plate is disposed such that the outer surface of the rotor 13 is on the same plane. Therefore, the interval of the gap (also referred to as an air gap) formed between the stator 12 and the rotor 13 is constant in the circumferential direction. The air gap is, for example, 100 to several tens of μm to several hundreds of μm depending on the size of the motor 5 or the like.

Next, the upper bearing 22 according to the present embodiment will be described in detail with reference to FIGS. 3 to 6.
The upper bearing 22 has a disk shape, and a cylindrical portion 37 through which the drive shaft 14 passes is provided at the center. The upper bearing 22 is provided such that the lower surface of the upper bearing 22 is in contact with the upper surface of the first cylinder main body 19, and the outer peripheral surface of the upper bearing 22 is fixed to the sealed container 2.
A refrigerant circulating portion 38 and a heat insulating portion 39 are formed on the upper surface of the upper bearing 22 on the motor 5 side.

The refrigerant flow portion 38 is a space surrounded by a recess 40 formed in a shape indented toward the lower surface on the upper surface side of the upper bearing 22 and a muffler plate 42 installed on the upper surface of the upper bearing 22.
Further, the heat insulating portion 39 is also formed in a shape that is recessed in the lower surface direction on the upper surface side of the upper bearing 22, and a recess 41 formed in a portion different from the recess 40 configuring the refrigerant flow portion 38 It is a space surrounded by

  The muffler plate 42 has a disk shape, and a through hole 43 through which the cylindrical portion 37 of the upper bearing 22 penetrates is formed at the center.

  The recessed portions 40 and 41 formed on the upper surface side of the upper bearing 22 are surrounded by the outer peripheral wall 44, the center wall 45, and the partition rib 46. The outer peripheral wall 44 is substantially parallel to the outer peripheral surface of the upper bearing 22 and has an arc shape. The center wall 45 is substantially parallel to the outer peripheral surface of the cylindrical portion 37 and in an arc shape.

  The partition rib 46 is formed in two different directions from the center side of the upper bearing 22 along the radial direction of the upper bearing 22. The partition rib 46 is provided between the outer peripheral wall 44 and the center wall 45. The partition rib 46 is provided so as to protrude from the flat surface of the upper bearing 22. As a result, the upper bearing 22 is in a state in which ribs along the radial direction are formed on one side, and the rigidity of the upper bearing 22 is improved as compared to the case where the upper bearing 22 has no ribs.

  The discharge hole 47 is formed in the upper bearing 22 in the refrigerant flow portion 38. A discharge valve (not shown) is installed in the discharge hole 47. The refrigerant discharged from the first cylinder chamber 17 is supplied to the refrigerant flow part 38 through the discharge hole 47. The refrigerant is temporarily stored in the refrigerant circulation unit 38 and then discharged from the refrigerant circulation unit 38 to the motor 5 side in the sealed container 2 through the discharge holes 48 formed in the muffler plate 42.

  The heat insulating portion 39 is separated from the refrigerant circulating portion 38 by the partition rib 46, and inside the heat insulating portion 39, the refrigerant discharged from the first cylinder chamber 17 or the second cylinder chamber 18 like the refrigerant circulating portion 38 The refrigerant is not supplied, and the refrigerant does not flow from the refrigerant circulation unit 38.

  In the heat insulating portion 39, a rib (first rib) 49 is provided, and the rib 49 is formed along the radial direction of the upper bearing 22. Therefore, at least three rib-like portions protruding in the radial direction are formed in the circumferential direction on the upper surface of the upper bearing 22 in combination with the two partition ribs 46. Thus, the upper surface of the upper bearing 22 is reinforced not only by the partition rib 46 but also by the rib 49 of the heat insulating portion 39, and the rigidity of the upper bearing 22 is improved. As a result, compared to the case where two rib-like portions are provided, bending mode is less likely to appear in the low frequency region, and resonance is less likely to occur.

  The height of the rib 49 may be a height from the bottom of the recess 41 to contact with the lower surface of the muffler plate 42 or may be a height not contacting the lower surface of the muffler plate 42. The higher the height of the rib 49, the higher the rigidity of the upper bearing 22 can be.

  It is desirable that the angle between the adjacent ribs 49 and the partition rib 46 or the angle between the adjacent partition ribs 46 be less than 180 °. In this case, bending mode is less likely to appear in the low frequency region and resonance is less likely to occur, as compared to the case where the angle is 180 degrees.

  In the upper bearing 22, a through hole 50 is formed at a location other than the refrigerant flow portion 38 and the heat insulating portion 39. The refrigerant from the second cylinder chamber 18 flows through the through hole 50. The refrigerant that has passed through the through hole 50 is discharged into the muffler 32.

  A plurality of bolt holes 51 are formed in the upper bearing 22. A bolt passing through the muffler plate 42, the first cylinder main body 19 and the second cylinder main body 20, the partition plate 21, the upper bearing 22 and the lower bearing 23 passes through the bolt holes 51, and these bolts are used to The components are clamped together.

  As described above, according to the present embodiment, as shown in FIG. 7, in the upper bearing 22, the heat insulating portion 39 in which the refrigerant does not flow is formed separately from the refrigerant flowing portion 38 in which the refrigerant flows. It is separated from the refrigerant circulating portion 38 by a partition rib 46 formed along the radial direction of the upper bearing 22, a muffler plate 42 installed on the upper surface side of the upper bearing 22, and the like. Further, since air or refrigerant oil having a temperature lower than that of the refrigerant discharged from the first cylinder chamber 17 exists inside the heat insulation portion 39, the heat insulation portion 39 becomes a heat insulation space in which the heat of the refrigerant is difficult to transmit. . FIG. 7 is a schematic longitudinal sectional view showing the upper bearing and the muffler plate of the compressor according to the present embodiment.

  Therefore, the heat insulating portion 39 reduces the temperature rise of the first and second compression mechanisms 6A, 6B due to the refrigerant discharged from the first cylinder chamber 17, the refrigerant on the motor 5 side, etc. The temperature rise of the refrigerant drawn into the two-cylinder chamber 18 can be reduced. Further, the refrigerant circulating unit 38 temporarily stores the refrigerant discharged from the first cylinder chamber 17, attenuates the sound when the refrigerant is discharged, and exhibits the muffling effect.

Second Embodiment
Next, with reference to FIGS. 8 to 10, a compressor according to a second embodiment of the present invention will be described. The detailed description of the components overlapping with the first embodiment will be omitted.

  In the first embodiment described above, the case where the rib is not formed in the refrigerant flow portion 38 has been described, but the present invention is not limited to this example, and in the present embodiment, the rib (second rib in the refrigerant flow portion 38) ) 52 is formed.

  Specifically, the ribs 52 in the refrigerant flow portion 38 are formed along the radial direction of the upper bearing 22. Thus, on the upper surface of the upper bearing 22, the rib-like portions protruding in the radial direction of the upper bearing 22 are not only the partition rib 46 and the ribs 49 of the heat insulating portion 39 but also the ribs 52 of the refrigerant circulating portion 38 It is formed. Thereby, at least four rib-like portions protruding in the radial direction are formed on the upper surface of the upper bearing 22 in the circumferential direction. Thereby, the rigidity of the upper bearing 22 is improved. As a result, compared to the case where two or three rib-like portions are provided, bending mode is less likely to appear at low frequency, and resonance is less likely to occur.

  The ribs 52 formed in the refrigerant flow portion 38 have a height not in contact with the muffler plate 42. Thus, although the ribs 52 are formed in the refrigerant flow portion 38, the refrigerant can flow in the refrigerant flow portion 38.

The refrigerant flow portion 38 is divided into a first separation space 38A and a second separation space 38B with the rib 52 interposed therebetween.
The discharge hole 53 is formed in the first separation space 38A of the refrigerant flow portion 38 in the upper bearing 22, and the discharge hole 54 is formed in the second separation space 38B. A discharge valve (not shown) is installed in the discharge hole 53 formed in the first separation space 38A. The refrigerant discharged from the first cylinder chamber 17 is supplied to the first separation space 38A through the discharge hole 53, and the refrigerant discharged from the second cylinder chamber 18 through the discharge hole 54 is the second separation space 38B. Supplied to
In the muffler plate 42, one discharge hole 55 is formed on the side of the first separation space 38A.

  The refrigerant is temporarily stored in the inside of the first separation space 38A of the refrigerant flow part 38 and in the inside of the second separation space 38B. The refrigerant stored in the second separation space 38B flows to the first separation space 38A, and merges with the refrigerant stored inside the first separation space 38A. Then, it is discharged from the first separation space 38A to the motor 5 side in the sealed container 2 through the discharge hole 55 formed on the muffler plate 42 on the side of the first separation space 38A.

  Only one discharge hole 55 formed in the muffler plate 42 may be formed not on the side of the first separation space 38A, but on the side of the second separation space 38B. In this case, the refrigerant flows from the first separation space 38A to the second separation space 38B.

  According to the present embodiment, since the refrigerant discharged from the first cylinder chamber 17 and the refrigerant discharged from the second cylinder chamber 18 merge in the refrigerant circulation unit 38, the refrigerant is merged outside the upper bearing 22. There is no need to provide a separate member.

  In addition, since the refrigerant from the second cylinder chamber 18 is introduced into the second separation space 38B, the number of muffler stages is increased, unlike the first embodiment in which the refrigerant passes through the through holes 50 of the upper bearing 22 and is discharged to the outside. Do. Therefore, in the compressor according to the present embodiment, the noise reduction effect is improved.

  Furthermore, also in the present embodiment, as shown in FIG. 10, in the upper bearing 22, a heat insulating part 39 in which the refrigerant does not flow is formed separately from the refrigerant flowing part 38 in which the refrigerant flows. It is separated from the refrigerant circulating portion 38 by a partition rib 46 formed along the radial direction of the upper bearing 22, a muffler plate 42 installed on the upper surface side of the upper bearing 22, and the like. Further, since air or refrigerant oil having a temperature lower than that of the refrigerant discharged from the first cylinder chamber 17 or the second cylinder chamber 18 is present in the heat insulation portion 39, the heat insulation portion 39 transmits the heat of the refrigerant. It becomes a difficult adiabatic space.

  Therefore, the heat insulating portion 39 reduces the temperature rise of the first and second compression mechanisms 6A, 6B due to the refrigerant discharged from the first cylinder chamber 17 and the second cylinder chamber 18, the refrigerant on the motor 5 side, etc. The temperature rise of the refrigerant drawn into the first cylinder chamber 17 and the second cylinder chamber 18 can be reduced.

In the above description, the refrigerant discharged from the second cylinder chamber 18 is supplied to the second separation space 38B, but the present invention is not limited to this example. For example, the refrigerant discharged from the second cylinder chamber 18 is not supplied to the refrigerant flow portion 38, and the discharge hole 56 is formed in the upper bearing 22 only in the second separation space 38B as shown in FIG. The refrigerant discharged from the first cylinder chamber 17 may be supplied to the second separation space 38B via 56.
In the muffler plate 42, one discharge hole 57 is formed on the side of the first separation space 38A.

  In this case, the refrigerant is temporarily stored inside the second separation space 38B of the refrigerant flow portion 38, and flows to the first separation space 38A. Then, the fluid is discharged from the first separation space 38A to the motor 5 side in the sealed container 2 through the discharge hole 57 formed on the muffler plate 42 on the side of the first separation space 38A.

  As in the first embodiment, the refrigerant from the second cylinder chamber 18 passes through the through hole (not shown) of the upper bearing 22 as it is without being stored in the refrigerant flow portion 38, and the inside of the sealed container 2 It is discharged to the motor 5 side of.

  Although in the embodiment described above, the rib 52 is provided at a height not in contact with the muffler plate 42 along the radial direction of the upper bearing 22, the present invention is not limited to this example. For example, as shown in FIG. 12, the rib 52 is formed with a notch 58 cut out in a part in the radial direction, and the other part of the rib 52 is provided at a height contacting the muffler plate 42. May be In this case, the refrigerant flows between the first separation space 38A and the second separation space 38B through the notches 58 formed in the rib 52.

  According to this modification, the rigidity of the upper bearing 22 can be enhanced as compared with the case where the heights of the ribs 52 are all lowered along the radial direction of the upper bearing 22. In addition, since the muffler plate 42 and the rib 52 are in contact with each other, deformation of the plate-like muffler plate 42 is not easily generated, and the flow passage area can be kept constant over a long period of time, and the reliability is also improved. Furthermore, the area through which the refrigerant flows between the first separation space 38A and the second separation space 38B can be easily reduced, and the muffling effect can be enhanced.

  In the embodiment described above, the height of the rib 52 is lowered or the notch 58 is formed in a part of the rib 52 to circulate the refrigerant, but the present invention is not limited to this example. It is not limited. For example, as shown in FIG. 13, the groove 59 may be formed at a position corresponding to the position of the rib 52 on the surface of the muffler plate 42 on the refrigerant flow portion 38 side. The groove 59 and the rib 52 are provided separately from each other, and the coolant flows between the groove 59 and the rib 52.

  According to this modification, since the refrigerant flows between the first separation space 38A and the second separation space 38B through the groove 59 formed in the muffler plate 42, the height of the rib 52 is not reduced. May be Therefore, the rigidity of the upper bearing 22 can be enhanced as compared with the case where the heights of the ribs 52 are all lowered along the radial direction of the upper bearing 22 or when the notches 58 are formed in a part of the ribs 52. .

  Further, the groove portion 59 formed in the muffler plate 42 may be formed by bending a portion corresponding to the groove portion 59 with respect to the muffler plate 42 made of a thin plate. In this case, the rigidity of the muffler plate 42 can be enhanced as compared to the muffler plate 42 not having the groove portion 59. Further, since the muffler plate 42 is integrally tightened by the upper bearing 22 and the bolt, the rigidity of the combination of the muffler plate 42 and the upper bearing 22 can also be enhanced.

  In addition, the groove part formed in the muffler board 42 is not restricted to formation by bending process, You may be formed by digging down the part corresponded to a groove part with respect to the flat muffler board 42 concavely.

  Furthermore, in the above-described embodiment, when the refrigerant flow portion 38 is provided with the first separation space 38A and the second separation space 38B, the case where the refrigerant flows between the first separation space 38A and the second separation space 38B will be described. However, the present invention is not limited to this example. The rib 52 is provided to be in contact with the muffler plate 42 in the radial direction of the upper bearing 22, and the first separation space 38A and the second separation space 38B may be separated by the rib 52.

In this case, as shown in FIG. 9, discharge holes 53 and 54 are formed in the upper bearing 22 in each of the first separation space 38A and the second separation space 38B of the refrigerant flow portion 38. A discharge valve is installed in the discharge hole 53 formed in the first separation space 38A.
Further, as shown in FIG. 14, discharge holes 60 and 61 are formed in the muffler plate 42 in the first separation space 38A and the second separation space 38B, respectively.

  The refrigerant discharged from the first cylinder chamber 17 through the discharge hole 53 is supplied to the first separation space 38A, and temporarily stored inside the first separation space 38A of the refrigerant circulation portion 38, and the muffler plate 42 It discharges from the 1st separation space 38A to the motor 5 side in sealed container 2 via discharge hole 60 formed in the 1st separation space 38A side. Further, the refrigerant discharged from the second cylinder chamber 18 through the discharge hole 54 is supplied to the second separation space 38B, and temporarily stored inside the second separation space 38B of the refrigerant circulation portion 38, and the muffler plate The second separation space 38 </ b> B discharges the second separation space 38 </ b> B to the motor 5 side in the sealed container 2 through the discharge hole 61 formed on the second separation space 38 </ b> B side.

  At this time, the refrigerant does not flow between the first separation space 38A and the second separation space 38B. Also in this case, the refrigerant is stored in each of the first separation space 38A and the second separation space 38B, so that the muffling effect is exhibited.

  In the embodiment described above, the case where the muffler 32 is installed is described, but the present invention is not limited to this example, and can be applied to the case where the muffler 32 is not installed. Further, in the embodiment described above, although the case of the multi-cylinder rotary compressor provided with a plurality of compression mechanisms has been described, the present invention can also be applied to the case where only one compression mechanism is provided.

Reference Signs List 1 compressor 2 closed container 5 motor 6 compression mechanism 6A first compression mechanism 6B second compression mechanism 8 discharge piping 9 accumulator 10, 11 suction piping 12 stator 13 rotor 14 drive shaft 17 first cylinder chamber 18 second cylinder chamber 19 1 cylinder body (cylinder body, 1 cylinder body)
20 2nd cylinder body (cylinder body, other cylinder body)
21 Partition plate 22 Upper bearing (bearing)
23 lower bearing 30, 31 suction port 32 muffler 37 cylindrical portion 38 refrigerant flow portion 38A first separation space (separation space, one separation space)
38 B Second separation space (separation space, other separation space)
39 heat insulation part 40, 41 recessed part 42 muffler plate (plate part)
43, 50 through hole 44 outer peripheral wall 45 central wall 46 partition rib (wall portion)
47, 48 discharge hole 49 rib (first rib)
51 bolt hole 52 rib (second rib)
53, 54, 55, 56, 57 Discharge holes 58 Notches 59 Grooves 60, 61 Discharge holes

Claims (5)

A cylinder body of a rotary compression mechanism,
A bearing provided on one side of the cylinder body for supporting a drive shaft;
A plate portion installed on one side of the bearing;
Equipped with
The bearing has a wall which is erected from the one surface of the bearing and is formed along the radial direction of the bearing.
A refrigerant circulating unit which is surrounded by the wall and the plate and through which the refrigerant discharged from the cylinder body flows;
A thermal insulation part which is separated from the refrigerant circulating part by the wall and the plate part while being surrounded by the wall part and the plate part, and the refrigerant does not circulate;
Is formed ,
In the bearing, a recess is formed by an outer peripheral wall of the bearing, a central wall of the bearing, and the wall portion,
The heat insulating portion is a space surrounded by the recess and the plate portion,
The compressor further includes a first rib which is erected from the one surface of the bearing in the heat insulating portion and formed along a radial direction of the bearing . At least two cylinder bodies are provided;
The bearing further includes a second rib which is erected from the one surface of the bearing in the refrigerant flow portion, and is formed along a radial direction of the bearing.
The refrigerant flow part is separated into at least two separation spaces by the second rib,
The compressor according to claim 1, wherein one of the separation spaces discharges the refrigerant from the one cylinder body, and the other separation space discharges the refrigerant from the other cylinder body. The compression according to claim 2 , wherein the refrigerant can flow from one side to the other in at least two of the separation spaces, and the plate portion is formed with a single discharge hole through which the refrigerant is discharged from the separation space. Machine. 4. The second rib according to claim 2 or 3 , wherein a notch partially cut out in the radial direction of the bearing is formed such that the refrigerant can flow from one to the other in at least two of the separated spaces. Description compressor. The compressor according to claim 2 or 3 , wherein a groove is formed in the plate portion at a position corresponding to the second rib such that the refrigerant can flow from one side to the other in at least two of the separation spaces.

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