JP4004278B2 - Rotary compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rotary compressor that compresses refrigerant in a refrigeration apparatus such as an air conditioner, a water heater, a car air conditioner, a showcase, a freezer / refrigerator, and a vending machine.
[0002]
[Prior art]
As this type of compressor, for example, an internal intermediate pressure type rotary two-stage compressor (hereinafter simply referred to as a compressor) 10X shown in FIG. 20 is well known. The compressor 10X includes an electric mechanism unit 14 including a stator 22, a rotor 24, and the like in the upper part of the hermetic container 12, and is connected to a lower part of the compressor 10X via the rotor 24 and the rotary shaft 16 of the electric mechanism unit 14. A two-stage rotary compression mechanism 18 is provided.
[0003]
In the two-stage rotary compression mechanism section 18 of the compressor 10X, a first compression mechanism section 32 is disposed on the lower side, and a second compression mechanism section 34 is disposed on the upper side, not shown. The gaseous refrigerant introduced from the accumulator through the refrigerant introduction pipe 92 is compressed by the first compression mechanism portion 32 on the lower stage side, and the compressed refrigerant is discharged into the sealed container 12, which is discharged through the refrigerant introduction pipe 94. The refrigerant is introduced into the second compression mechanism section 34 in the second stage, where it is further compressed to a high pressure and supplied from the refrigerant discharge pipe 96 to a refrigerant circuit of an air conditioner (not shown).
[0004]
In the compressor 10X, the refrigerant compressed by the first compression mechanism unit 32 is compressed to a higher pressure by the second compression mechanism unit 34, so that the refrigerant is compressed by the second compression mechanism unit 34 to a high pressure of about 12 MPaG, for example. The upper cover 68 that seals the discharge silencing chamber 64 of the upper cover member through which the gas passes passes is discharged from the lower support member 54 through which the gas compressed by the first compression mechanism 32 to a pressure of, for example, about 6 MPaG passes. It is thicker than the lower cover 66 that seals the chamber 62 to enhance pressure resistance.
[0005]
That is, in the conventional compressor 10X, the discharge silencer chamber 64 of the upper support member 56 through which the gas compressed to a high pressure passes is simply sealed by the upper cover 68 having a large plate thickness. There was a problem that increased.
[0006]
[Problems to be solved by the invention]
Therefore, it is necessary to improve the pressure resistance of the upper cover without causing an increase in mass, which has been a problem to be solved.
[0007]
[Means for Solving the Problems]
In order to solve the above-described problems of the prior art, the present invention includes a compression mechanism portion and an electric mechanism portion in a sealed container, and the compression mechanism portion seals the cylinder and both ends of the cylinder. With bearing An end face sealing member, a rotary shaft that is pivotally supported by the end face sealing member and rotated by the electric mechanism portion, is attached eccentrically to the rotary shaft, and the outer peripheral surface is in sliding contact with the inner peripheral surface of the cylinder, and the end surface is end face sealed. A roller that slides in contact with the inner surface of the stop member and rotates eccentrically, and is inserted and installed in a vane slot provided in the cylinder, abuts against the outer peripheral surface of the roller, and reciprocates following the eccentric rotation of the roller to move inside the cylinder in a low-pressure chamber And the sound deadening chamber of the end face sealing member through which the gas compressed in the cylinder passes are sealed. It is formed by a disk-shaped part and a cylindrical part provided in the center of the disk-shaped part and extending from a hole through which the bearing passes. A cover member and an outer surface of the cover member And formed radially from the outer periphery of the cylindrical part to the disk-like part A rotary compressor having a first configuration including a rib;
[0008]
Furthermore, a rotary compressor having a second configuration in which a compression mechanism unit is provided in a plurality of stages so that the refrigerant can be repeatedly compressed, and a cover member having a rib provided on the outer surface is provided in the subsequent compression mechanism part. ,
Is to provide.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of the present invention will be described in detail with reference to FIGS. In order to facilitate understanding, in these drawings, parts having the same functions as those described with reference to FIG.
[0010]
FIG. 1 is a longitudinal sectional view of an internal intermediate pressure type two-stage compression compressor 10 having first and second compression mechanisms 32 and 34 as an embodiment of the rotary compressor of the present invention, and FIG. 3 is a front view of the compressor 10, FIG. 4 is a side view of the compressor 10, FIG. 5 is another longitudinal sectional view of the compressor 10, and FIG. FIG. 7 is a plan sectional view of the electric mechanism portion 14 of the compressor 10, and FIG. 8 is an enlarged sectional view of the rotary compression mechanism portion 18 of the compressor 10.
[0011]
The compressor 10 includes a cylindrical airtight container 12 made of a steel plate, an electric mechanism portion 14 disposed and housed above the internal space of the airtight container 12, and an electric mechanism portion disposed below the electric mechanism portion 14. The rotary compression mechanism unit 18 includes a first compression mechanism unit 32 (first stage) driven by the rotation shaft 16 of the unit 14 and a second compression mechanism unit 34 (second stage) disposed thereon. It is comprised by.
[0012]
The height dimension of the compressor 10 of the embodiment is 220 mm (outer diameter 120 mm), the height dimension of the electric mechanism section 14 is about 80 mm (outer diameter 110 mm), and the height dimension of the rotary compression mechanism section 18 is about 70 mm (outside). The distance between the electric mechanism 14 and the rotary compression mechanism 18 is about 5 mm. Further, the excluded volume of the second compression mechanism section 34 is designed to be smaller than the excluded volume of the first compression mechanism section 32.
[0013]
In the embodiment, the sealed container 12 is formed of a steel plate having a thickness of 4.5 mm, and the bottom part is an oil storage part that stores the refrigerating machine oil 190, and the cylindrical container body 12A that houses the electric mechanism part 14 and the rotary compression mechanism part 18; The container body 12A has a substantially bowl-shaped end cap (lid) 12B that closes the upper opening of the container body 12A, and a circular mounting hole 12D is formed at the center of the upper surface of the end cap 12B. A terminal (wiring is omitted) 20 for supplying electric power to the electric mechanism portion 14 is attached to the attachment hole 12D.
[0014]
In this case, the end cap 12B around the terminal 20 is formed with a stepped portion 12C having a predetermined curvature in an annular shape by press-fitting. The terminal 20 includes a circular glass portion 20A through which the electrical terminal 139 is attached, and a metal attachment portion 20B formed around the glass portion 20A and projecting obliquely outward and downward in a bowl shape. It is configured. The thickness dimension of the mounting portion 20B is 2.4 ± 0.5 mm. And the terminal 20 inserts the glass part 20A into the mounting hole 12D from the lower side, faces the upper side, and attaches the mounting part 20B to the peripheral edge of the mounting hole 12D, and the peripheral edge of the mounting hole 12D of the end cap 12B. The attachment portion 20B is welded to the end cap 12B.
[0015]
The electric mechanism section 14 includes a stator 22 that is annularly attached along the inner peripheral surface of the upper space of the sealed container 12, and a rotor 24 that is inserted and arranged with a slight gap inside the stator 22. The rotor 24 is fixed to a rotating shaft 16 that passes through the center and extends in the vertical direction.
[0016]
The stator 22 includes a laminated body 26 in which donut-shaped electromagnetic steel plates are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method (FIG. 7). Similarly to the stator 22, the rotor 24 is also formed by a laminated body 30 of electromagnetic steel plates, and a permanent magnet 31 is inserted into the laminated body 30.
[0017]
An intermediate partition plate 36 is sandwiched between the first compression mechanism portion 32 and the second compression mechanism portion 34. That is, the first compression mechanism portion 32 and the second compression mechanism portion 34 include an intermediate partition plate 36, cylinders 38 and 40 disposed below and above the intermediate partition plate 36, and the cylinders 38 and 40. The eccentric portions 42 and 44 provided on the rotary shaft 16 with a phase difference of 180 degrees therein, the rollers 46 and 48 fitted into the eccentric portions 42 and 44 and rotated eccentrically, and the rollers 46 and 48 The bearings of the rotary shaft 16 are closed by closing the vane 50 that abuts and divides the cylinders 38 and 40 into the low-pressure chamber side and the high-pressure chamber side, the lower opening surface of the cylinder 38 and the upper opening surface of the cylinder 40, respectively. The lower support member 54 and the upper support member 56 are used as shaft support members that also serve as the shaft support members.
[0018]
The lower support member 54 and the upper support member 56 are formed with suction passages 58 and 60 that communicate with the inside of the cylinders 38 and 40 by suction ports 161 and 162, respectively, and recessed discharge silencer chambers 62 and 64. The openings of both discharge silencing chambers 62 and 64 are each closed by a cover. That is, the discharge silencer chamber 62 is closed by the lower cover 66, and the discharge silencer chamber 64 is closed by the upper cover 68.
[0019]
A bearing 54A is formed through the center of the lower support member 54, and a cylindrical bush 122 is mounted on the inner surface of the bearing 54A. Further, a bearing 56A is formed upright at the center of the upper support member 56, and a cylindrical bush 123 is also mounted on the inner surface of the bearing 56A. The bushes 122 and 123 are made of a material having a low frictional resistance, and the rotating shaft 16 is held by the bearings 54A of the lower support member 54 and the bearings 56A of the upper support member 56 through the bushes 122 and 123.
[0020]
In this case, the lower cover 66 is formed of a circular steel plate having a donut shape, and four peripheral bolts are fixed to the lower support member 54 from below with four main bolts 129. The lower surface opening of the discharge silencing chamber 62 communicating with the inside of the cylinder 38 of the compression mechanism 32 is closed. The tip of the main bolt 129 is screwed into the upper support member 56. The inner periphery of the lower cover 66 protrudes inwardly from the inner surface of the bearing 54A of the lower support member 54, whereby the lower end surface of the bush 122 is held by the lower cover 66 and is prevented from falling off (FIG. 10). FIG. 11 shows the lower surface of the lower support member 54, and 127 is a mounting groove for the discharge valve of the first compression mechanism 32 that opens and closes the discharge port 39 in the discharge silencer chamber 62.
[0021]
The lower support member 54 is formed of an iron-based sintered material (or a casting may be used), and the surface (lower surface) on which the lower cover 66 is attached is processed to a flatness of 0.1 mm or less, and then subjected to steam treatment. Has been added. Since the surface on which the lower cover 66 is attached is made of iron oxide by this steam treatment, the hole inside the sintered material is closed and the sealing performance is improved. This eliminates the need for a gasket between the lower cover 66 and the lower support member 54.
[0022]
The discharge silencer chamber 62 and the upper cover 68 in the sealed container 12 are communicated with each other by the communication path 63 which is a hole penetrating the cylinders 38 and 40 and the intermediate partition plate 36 (FIG. 5). . In this case, an intermediate discharge pipe 121 is erected at the upper end of the communication path 63, and the intermediate discharge pipe 121 is a gap between adjacent stator coils 28 wound around the stator 22 of the upper electric mechanism section 14. (FIG. 7).
[0023]
Further, the upper cover 68 closes the upper surface opening of the discharge silencing chamber 64 communicating with the inside of the cylinder 40 of the second compression mechanism section 34 by the discharge port 41, and the discharge silencing chamber 64 and the electric mechanism section 14 in the sealed container 12. Divide into sides. As shown in FIG. 2, the upper cover 68 has a cylindrical portion 68B extending upward from a hole through which the bearing 56A of the upper support member 56 is provided at the center of the disc-shaped portion 68A. A plurality of ribs 68C are provided radially from the outer periphery of the cylindrical portion 68B. Each rib 68C can also be seen as standing from the upper surface of the disc-shaped portion 68A. Further, four bolt holes 68D are formed. Then, with the beaded gasket 124 sandwiched between the upper support member 56 (FIG. 13), the peripheral portion is fixed to the upper support member 56 from above by the four main bolts 78 via the gasket 124. Has been. The tip of the main bolt 78 is screwed into the lower support member 54.
[0024]
Since the rigidity of the disk-shaped part 68A is remarkably improved by adopting the configuration related to the upper cover 68, the discharge silencer that has a higher pressure than the inside of the sealed container 12 while making the whole including the disk-shaped part 68A thin. Weight reduction can be achieved while sufficiently withstanding the pressure in the chamber 64. Further, an O-ring 126 is provided between the inner peripheral edge of the upper cover 68 and the outer surface of the bearing 56A (FIG. 13). By sealing the bearing 56A side with the O-ring 126, it becomes possible to sufficiently seal the inner periphery of the upper cover 68 and prevent gas leakage, and the volume of the discharge silencer chamber 64 can be increased. The ring eliminates the need to fix the inner peripheral edge of the upper cover 68 to the bearing 56A. In FIG. 12, reference numeral 128 denotes a mounting groove for the discharge valve of the second compression mechanism section 34 that opens and closes the discharge port 41 in the discharge silencer chamber 64.
[0025]
In the intermediate partition plate 36 that closes the upper opening surface of the cylinder 38 of the first compression mechanism portion 32 and the lower opening surface of the cylinder 40 of the second compression mechanism portion 34, the suction in the cylinder 40 As shown in FIGS. 14 and 15, a through-hole 131 is formed in the position corresponding to the side from the outer peripheral surface to the inner peripheral surface, and connects the outer peripheral surface and the inner peripheral surface to form an oil supply passage. The opening on the outer peripheral surface side is sealed by, for example, press-fitting a sealing material 132 into the outer peripheral surface side of the through hole 131. Further, a communication hole 133 extending upward from the middle part of the through hole 131 is formed.
[0026]
On the other hand, a communication hole 134 communicating with the communication hole 133 of the intermediate partition plate 36 is formed in the suction port 162 (suction side) of the cylinder 40. Further, as shown in FIG. 8, a vertical oil hole 80 and lateral oil supply holes 81 and 82 communicating with the oil hole 80 are provided in the rotary shaft 16 as shown in FIG. The opening on the inner peripheral surface side of the 36 through-hole 131 communicates with the oil hole 80 through these oil supply holes 81 and 82.
[0027]
In addition, oil supply holes 83 and 84 communicating with the oil hole 80 are also provided in the eccentric portions 42 and 44 of the rotating shaft 16. And the groove part of the axial direction and the groove part of the circumferential direction which cross | intersects the groove part are provided in the part in which the oil supply holes 83 and 84 are opened.
[0028]
That is, the groove portion 43A in the axial direction and the circumferential groove portion 43B intersecting with the groove portion 43A are provided in the portion where the oil supply hole 83 is opened, and the axial groove portion is provided in the portion where the oil supply hole 84 is opened. 45A and a circumferential groove 45B intersecting with the groove 45A are provided.
[0029]
Therefore, the rotary shaft 16 is pumped from the bottom of the sealed container 12 through the oil hole 80 of the rotary shaft 16 and discharged, for example, from the oil supply hole 84 of the eccentric portion 44 of the second compression mechanism portion 34. The refrigerating machine oil 190 that has entered the portion of the groove 45B opposite to the rotation direction is left behind from the end portion of the groove 45B rather than the axial direction as the rotation shaft 16 rotates, so that the eccentric portion 44 of the rotation shaft 16 rotates. Since it easily enters the circumferential direction between the outer peripheral surface and the inner peripheral surface of the roller 48, the rotational load is large, so that the eccentric portion 44 of the rotating shaft 16 and the roller 48 attached to the eccentric portion 44 are in close contact with each other. Even if it slides, it enters between them, and lubrication between the eccentric portion 44 of the rotating shaft 16 and the roller 48 is effectively performed (oil supply hole of the eccentric portion 42 of the first compression mechanism portion 32 having a small rotational load). Refrigerator discharged from 83 190 also acts in the same way).
[0030]
In addition, since the inside of the closed container 12 during operation is at an intermediate pressure, it is difficult to supply the refrigerating machine oil 190 into the cylinder 40 that is at a high pressure for performing the second stage compression. With this configuration, the refrigeration oil 190 that has been pumped up from the oil storage section at the inner bottom of the sealed container 12 and raised through the oil hole 80 and discharged from the oil supply holes 81 and 82 enters the through hole 131 of the intermediate partition plate 36 and communicates therewith. The holes 133 and 134 are supplied to the suction side (suction port 162) of the cylinder 40 to be used for lubricating the sliding portion.
[0031]
In FIG. 17, L indicates the pressure fluctuation on the suction side of the cylinder 40 of the second compression mechanism 34, and P <b> 1 indicates the pressure on the inner peripheral surface of the intermediate partition plate 36. As indicated by L1 in this figure, the pressure (suction pressure) on the suction side of the cylinder 40 is lower than the pressure on the inner peripheral surface side of the intermediate partition plate 36 due to suction pressure loss during the suction process. During this period, oil is supplied into the cylinder 40 from the through hole 131 and the communication hole 133 of the intermediate partition plate 36 through the communication hole 134 of the cylinder 40.
[0032]
As described above, the cylinders 38 and 40, the intermediate partition plate 36, the support members 54 and 56, and the covers 66 and 68 are fastened from above and below by the four main bolts 78 and the main bolts 129. 40, the intermediate partition plate 36, and the support members 54 and 56 are fastened by auxiliary bolts 136 positioned outside these main bolts 78 and 129 (FIG. 5). The auxiliary bolt 136 is inserted from the upper support member 56 side, and the tip thereof is screwed to the lower support member 54.
[0033]
The auxiliary bolt 136 is positioned in the vicinity of the vane slot 70 described later of the vane 50. Thus, by adding the auxiliary bolt 136 and integrating the rotary compression mechanism portion 18, the sealing performance against the extremely high pressure inside is ensured, and the vicinity of the vane slot 70 of the vane 50 is secured. Since the tightening is performed, leakage of a high back pressure applied to the vane 50 can be prevented.
[0034]
On the other hand, a vane slot 70 for storing the vane 50 and a storage portion 70A for storing a spring 76 as a spring member located outside the vane slot 70 are formed in the cylinder 40, and the storage portion 70A. Is open to the vane slot 70 side and the closed container 12 (container body 12A) side (FIG. 9). The spring 76 is in contact with the outer end of the vane 50 and constantly urges the vane 50 toward the roller 48. A metal plug 137 is provided in the housing portion 70A of the spring 76 on the closed container 12 side, and serves to prevent the spring 76 from coming off.
[0035]
In this case, the outer dimension of the plug 137 is set smaller than the inner dimension of the storage portion 70A, and the plug 137 is inserted into the storage portion 70A by a clearance fit. An O-ring 138 is attached to the peripheral surface of the plug 137 for sealing between the plug 137 and the inner surface of the storage portion 70A. The distance between the outer end of the cylinder 40, that is, the outer end of the storage portion 70A and the container body 12A of the sealed container 12 is set to be smaller than the distance from the O-ring 138 to the end of the plug 137 on the sealed container 12 side. Has been. A high pressure, which is the discharge pressure of the second compression mechanism 34, is applied as a back pressure to a back pressure chamber (not shown) communicating with the vane slot 70 of the vane 50. Accordingly, the plug 137 has a high pressure on the spring 76 side and an intermediate pressure on the sealed container 12 side.
[0036]
With such a dimensional relationship, as in the case where the plug 137 is press-fitted and fixed in the housing portion 70A, the cylinder 40 is deformed, the sealing performance with the upper support member 56 is lowered, and the performance is deteriorated. It will be possible to avoid it. Even with such a clearance fit, the distance between the cylinder 40 and the sealed container 12 is set to be smaller than the distance from the O-ring 138 to the end of the plug 137 on the sealed container 12 side. Even if the plug 137 moves in the direction in which the plug 137 is pushed out of the storage portion 70A due to the high pressure (back pressure of the vane 50), the O-ring 138 is still positioned in the storage portion 70A when the movement is prevented by contact with the hermetic container 12. Therefore, no problem occurs in the function of the plug 138.
[0037]
Incidentally, the connecting portion 90 that connects the eccentric portions 42 and 44 formed integrally with the rotating shaft 16 with a phase difference of 180 degrees has a cross-sectional area larger than the circular cross section of the rotating shaft 16. Therefore, in order to give rigidity, it is formed into a non-circular shape such as a rugby ball (FIG. 18). That is, the cross-sectional shape of the connecting portion 90 that connects the eccentric portions 42 and 44 provided on the rotating shaft 16 is increased in thickness in a direction perpendicular to the eccentric direction of the eccentric portions 42 and 44 (the hatched portion in the figure). ).
[0038]
As a result, the cross-sectional area of the connecting portion 90 that connects the eccentric portions 42 and 44 that are integrally adjacent to the rotating shaft 16 is increased, and the secondary moment is increased to increase the strength (rigidity), thereby improving durability and reliability. Improves sex. In particular, when a refrigerant having a high operating pressure is compressed in two stages, the load acting on the rotary shaft 16 increases due to the large pressure difference between the high and low pressures. In addition, the rotating shaft 16 is prevented from being elastically deformed.
[0039]
In this case, if the center of the lower eccentric portion 42 is O1, and the center of the upper eccentric portion 44 is O2, the center of the arc of the surface of the connecting portion 90 on the eccentric direction side of the eccentric portion 42 is O1, and the eccentric portion 44. The center of the arc of the surface of the connecting portion 90 on the eccentric direction side is O2. Thus, when the eccentric part 42, 44 and the connecting part 90 are cut by fixing the rotating shaft 16 to the cutting machine, after machining the eccentric part 42, only one radius is changed to process one surface of the connecting part 90. Then, it becomes possible to change the fixed position to process the other surface of the connecting portion 90 and change only the radius to process the eccentric portion 44. As a result, the number of times of fixing the rotating shaft 16 is reduced, and the productivity is remarkably improved.
[0040]
The suction passages 58 and 60 of the lower support member 54 and the upper support member 56, the discharge silencer chamber 64, and the upper cover 68 on the curved side surface of the container main body 12A of the sealed container 12 (corresponding substantially to the lower end of the electric mechanism unit 14). Cylindrical sleeves 141 to 144 are fixed by welding at positions corresponding to (position). The sleeve 142 is provided at a position approximately 90 degrees away from the sleeve 141, the sleeve 143 is provided above the sleeve 141, and the sleeve 144 is provided at a position substantially facing the sleeve 141.
[0041]
In the sleeve 141, one end of a refrigerant introduction pipe 92 for introducing refrigerant gas into the cylinder 38 of the first compression mechanism section 32 is inserted and connected. One end of the refrigerant introduction pipe 92 is connected to the suction passage 58 of the cylinder 38. It is communicated to. The other end of the refrigerant introduction pipe 92 is connected to the lower end of the accumulator 204.
[0042]
Also, one end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the cylinder 40 of the second compression mechanism section 34 is inserted into and connected to the sleeve 143, and one end of the refrigerant introduction pipe 94 is connected to the suction passage 60 of the cylinder 40. It is communicated to. The refrigerant introduction pipe 94 passes through the upper side of the sealed container 12 and extends from the sleeve 142, and the other end is inserted and connected into the sleeve 142 to communicate with the sealed container 12. In addition, a refrigerant discharge pipe 96 is inserted and connected into the sleeve 144, and one end of the refrigerant discharge pipe 96 communicates with the discharge silencer chamber 64.
[0043]
The accumulator 204 is a tank that performs gas-liquid separation of the sucked refrigerant. 12 sideways.
[0044]
The refrigerant introduction pipe 92 inserted and connected to the sleeve 141 and the refrigerant introduction pipe 94 inserted and connected to the sleeve 143 are drawn to the opposite sides in the vicinity of the sleeves 141 and 143. That is, as shown in FIG. 4, the refrigerant introduction pipe 92 extending from the accumulator 204 is bent in the right direction in the drawing to reach the sleeve 141, and the other refrigerant introduction pipe 94 is bent in the left direction in the drawing to form the sleeve 143. Thus, even if the vertical dimension of the accumulator 204 is increased to increase the volume, the refrigerant introduction pipes 92 and 94 do not interfere with each other.
[0045]
Further, a screw groove 151 is formed on the outer peripheral portion of the sleeve 141, and a collar portion 152 is formed on the outer peripheral portion of the sleeves 142, 143, and 144. A connector for connecting the airtight test pipe can be screwed into the thread groove 151, and a coupler for connecting the airtight test pipe can be detachably engaged with the flange 152.
[0046]
By adopting such a configuration, an airtight test pipe from a compressed air generating device (not shown) can be easily connected using a coupler or a connector, so that the airtight test can be completed in a short time. become. In particular, in the sleeves 141 and 143 adjacent in the vertical direction, one sleeve 141 is formed with a thread groove 151 and the other sleeve 143 is formed with a flange 152, so that two couplers larger in size than the connector are provided. Even when the sleeves 141 and 143 are narrowly spaced, the airtight test pipe can be connected to each of the sleeves 141 and 143 using the narrow space.
[0047]
As a refrigerant of the compressor 10, carbon dioxide (CO 2) as an example of carbon dioxide, which is a natural refrigerant, satisfies the requirements of being friendly to the global environment, non-combustible and non-toxic. ₂ As the refrigerating machine oil 190 as the lubricating oil, for example, existing oils such as mineral oil (mineral oil), alkylbenzene oil, ether oil, ester oil are used.
[0048]
The compressor 10 having the above-described configuration shown in the embodiment is used in a refrigerant circuit of an in-vehicle cooling apparatus 200 as shown in FIG. 19, for example. That is, the refrigerant discharge pipe 96 of the compressor 10 is connected to the inlet of an air-cooled gas cooler 201. The refrigerant pipe exiting the gas cooler 201 is connected to the inlet of the evaporator 203 via an expansion valve 202 as a decompression device, and the refrigerant introduction pipe 92 is connected to the outlet of the evaporator 203. In FIG. 19, the accumulator 204 is omitted.
[0049]
Next, the operation of the cooling device 200 shown in FIG. 19 will be described. When the stator coil 28 of the electric mechanism unit 14 is energized through the terminal 20 of the compressor 10 and a wiring (not shown), the electric mechanism unit 14 is activated and the rotor 24 rotates. By this rotation, the rollers 46 and 48 fitted to the eccentric portions 42 and 44 provided integrally with the rotary shaft 16 are eccentrically rotated in the cylinders 38 and 40.
[0050]
For this reason, the low-pressure (first-stage suction pressure LP: 4 MPaG) refrigerant gas sucked from the suction port 161 to the low-pressure chamber side of the cylinder 38 through the refrigerant introduction pipe 92 and the suction passage 58 formed in the lower support member 54. Is compressed by the operation of the roller 46 and the vane 50 to become an intermediate pressure (MP1: 8 MPaG) from the high pressure chamber side of the cylinder 38 through the discharge port 39 and the discharge silencer chamber 62 formed in the lower support member 54 through the communication path 63. It is discharged from the intermediate discharge pipe 121 into the sealed container 12.
[0051]
At this time, since the intermediate discharge pipe 121 is directed to the gap between the adjacent stator coils 28 wound around the stator 22 of the upper electric mechanism section 14, refrigerant gas having a relatively low temperature is still supplied to the electric mechanism section. 14 can be actively supplied, and the temperature rise of the electric mechanism unit 14 is suppressed. Moreover, the inside of the airtight container 12 becomes intermediate pressure (MP1) by this.
[0052]
The intermediate pressure refrigerant gas in the sealed container 12 exits from the sleeve 142 (intermediate discharge pressure is MP1), and the suction port 162 passes through the refrigerant introduction pipe 94 and the suction passage 60 formed in the upper support member 56. To the low pressure chamber side of the cylinder 40 (second-stage suction pressure MP2). The suctioned intermediate-pressure refrigerant gas is compressed in the second stage by the operation of the roller 48 and the vane 50 to become a high-temperature and high-pressure refrigerant gas (second-stage discharge pressure HP: 12 MPaG), and is discharged from the high-pressure chamber side. The gas flows into the gas cooler 201 through the discharge silencer chamber 64 formed in the upper support member 56 and the refrigerant discharge pipe 96. The refrigerant temperature at this time has increased to about 100 ° C., and the high-temperature and high-pressure refrigerant gas is radiated and cooled, and exits the gas cooler 201.
[0053]
Then, after being depressurized by the expansion valve 202, it flows into the evaporator 203 and evaporates. The air in the vehicle is cooled by the heat of vaporization that the refrigerant removes from the surroundings at the time of evaporation in the evaporator 203 to perform cooling. The refrigerant vapor evaporated in the evaporator 203 repeats a cycle of being sucked into the first compression mechanism section 32 from the refrigerant introduction pipe 92 via the accumulator 204 (not shown in FIG. 19).
[0054]
In addition, since this invention is not limited to the said embodiment, various deformation | transformation implementation is possible in the range which does not deviate from the meaning as described in a claim.
[0055]
For example, the ribs 68C provided on the upper cover 68 may be provided on the upper surface of the disk-shaped part 68A concentrically with the cylindrical part 68B. At this time, the cylindrical portion 68B is not necessarily provided. Moreover, it is also possible to use a rib provided in a circumferential shape and a rib provided in the radial direction in combination.
[0056]
Further, the gas cooler 201 is configured to be able to use the heat radiated from the high-temperature and high-pressure refrigerant gas, and the compressor 10 is used as a compressor of an air conditioner capable of (1) heating operation, and (2) a hot water supply device It is also possible to use it as a compressor.
[0057]
Further, when the compressor 10 is used as a compressor of a refrigeration apparatus, hydrofluorocarbon (HFC), hydrochlorofluorocarbon (HCFC), or the like may be used as a refrigerant.
[0058]
【The invention's effect】
As described above, the rotary compressor of the present invention is a compressor in which ribs are provided on the outer surface of the cover member that seals the sound deadening chamber of the end surface sealing member through which the gas compressed in the cylinder passes. Yes, because it is a compressor in which the compression mechanism unit is installed in a plurality of stages so that the gas taken in from the outside can be repeatedly compressed, and the cover member with the rib provided on the outer surface is provided in the subsequent compression mechanism part. The rigidity of the cover member is significantly improved. Therefore, the cover member can be made thinner and lighter.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a compressor according to the present invention.
FIG. 2 is a perspective view of a cover member used in the compressor of the present invention.
FIG. 3 is a front view of the compressor of FIG. 1;
4 is a side view of the compressor of FIG. 1. FIG.
FIG. 5 is another longitudinal sectional view of the compressor of FIG. 1;
6 is still another longitudinal sectional view of the compressor of FIG. 1. FIG.
7 is a plan sectional view of an electric mechanism portion of the compressor of FIG. 1. FIG.
8 is an enlarged cross-sectional view of a rotary compression mechanism portion of the compressor of FIG.
9 is an enlarged cross-sectional view of a vane portion of a second compression mechanism portion of the compressor of FIG.
10 is a cross-sectional view of a lower support member and a lower cover of the compressor of FIG.
11 is a bottom view of a lower support member of the compressor of FIG.
12 is a top view of an upper support member and an upper cover of the compressor of FIG. 1. FIG.
13 is a cross-sectional view of an upper support member and an upper cover of the compressor of FIG.
14 is a top view of an intermediate partition plate of the compressor in FIG. 1. FIG.
15 is a cross-sectional view taken along line AA in FIG.
16 is a top view of a cylinder of the compressor in FIG. 1. FIG.
FIG. 17 is a diagram showing pressure fluctuation on the suction side of the cylinder of the compressor of FIG. 1;
18 is an explanatory cross-sectional view showing a connecting portion of a rotating shaft of the compressor shown in FIG. 1;
FIG. 19 is a refrigerant circuit diagram of an air conditioner to which the compressor of FIG. 1 is applied.
FIG. 20 is an explanatory diagram showing a conventional technique.
[Explanation of symbols]
10, 10X (rotary) compressor
12 Sealed container
12A Container body
12B End cap
14 Electric mechanism
16 Rotating shaft
18 Rotary compression mechanism
20 terminal
22 Stator
24 Rotor
26 Laminate
28 Stator Coil
30 Laminate
31 Permanent magnet
32 1st compression mechanism part
34 Second compression mechanism
36 Intermediate divider
38, 40 cylinders
39, 41 Discharge port
42 Eccentric part
43A, 43B Groove
44 Eccentric part
45A, 45B Groove
46, 48 rollers
50 Vane
54 Lower support member
54A Bearing
56 Upper support member
58, 60 Suction passage
62 Discharge silencer
63 communication path
64 Discharge silencer
66 Bottom cover
68 Top cover
68A disk-shaped part
68B cylindrical part
68C rib
68D bolt hole
70 vane slot
70A storage unit
76 Spring (spring member)
78, 129 Main bolt
80 Oil hole
81, 82, 83, 84 Refueling hole
90 connecting part
92, 94 Refrigerant introduction pipe
96 Refrigerant discharge pipe
121 Intermediate discharge pipe
131 Through hole (oil supply passage)
132 Sealant
133, 134 communication hole
137 plug
138 O-ring
141, 142, 143, 144 sleeve
147 Bracket
152 buttock
151 thread groove
161, 162 Suction port
190 Refrigerating machine oil
200 Air conditioner
201 gas cooler
202 expansion valve
203 Evaporator
204 Accumulator
205 Bracket

Claims (2)

The airtight container includes a compression mechanism portion and an electric mechanism portion, and the compression mechanism portion is pivotally supported by a cylinder, an end surface sealing member having a bearing that seals both ends of the cylinder, and the end surface sealing member. A rotating shaft that is rotated by the electric mechanism, a roller that is eccentrically attached to the rotating shaft, has an outer peripheral surface that is in sliding contact with the inner peripheral surface of the cylinder, and an end surface that is in sliding contact with the inner surface of the end surface sealing member; The vane is inserted into the vane slot provided in the cylinder and abuts against the outer peripheral surface of the roller, reciprocates following the eccentric rotation of the roller, and the vane partitions the cylinder into a low pressure chamber and a high pressure chamber, and is compressed in the cylinder. A cover formed by a disk-shaped part that seals the silencer chamber of the end surface sealing member through which the gas passes and a cylindrical part that is provided at the center of the disk-shaped part and extends from a hole through which the bearing passes. Member and the outer surface of the cover member Rotary compressor, characterized in that a rib formed radially in a disc-shaped portion from the outer periphery of the cylindrical portion Te.   2. The rotary compressor according to claim 1, wherein the compression mechanism section is provided in a plurality of stages so that the refrigerant can be repeatedly compressed, and a cover member having a rib provided on the outer surface is provided in the subsequent compression mechanism section.

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