JP4401365B2 - Rotary compressor - Google Patents

Description

  The present invention includes first and second rotary compression elements driven by an electric element in a sealed container, and compresses the intermediate pressure gas discharged by the first rotary compression element and discharged into the sealed container. The present invention relates to a rotary compressor that compresses with two rotary compression elements.

Conventionally, this type of rotary compressor is provided with first and second rotary compression elements at the lower part of the hermetic container and an electric element at the upper part, and the rotation of the cylinder and the support member and the electric element for closing the opening surface under the cylinder. A roller that rotates along the inner wall of the cylinder by an eccentric portion integrally formed with the shaft, and a vane that reciprocally slides in a groove provided in the cylinder with the tip abutting against the roller. The rotary compression element, the cylinder, the support member that closes the opening surface on the cylinder, and the eccentric portion provided in the first rotary compression element that are integrally formed with the rotary shaft of the electric element are provided 180 degrees opposite to each other. The second rotary compression element is composed of a roller that rotates along the inner wall of the cylinder by the eccentric portion, and a vane that reciprocally slides in a groove provided in the cylinder with the tip abutting against the roller. It is. (For example, see Patent Document 1)
Japanese Patent Laid-Open No. 2-294857

  Gas (refrigerant gas) is sucked into the low-pressure chamber side of the cylinder from the suction port of the first rotary compression element, and is compressed by the operation of the roller and vane to become an intermediate pressure from the high-pressure chamber side of the cylinder. It is discharged into the sealed container through the chamber. The intermediate pressure gas discharged into the hermetic container is sucked into the low pressure chamber side of the cylinder from the suction port of the second rotary compression element, and the second stage compression is performed by the operation of the roller and the vane, and the high temperature and high pressure gas. Then, it is discharged from the high pressure chamber side through the discharge port and the discharge silencer chamber.

  The gas discharged from the rotary compressor flows into the radiator of the refrigerant circuit, radiates heat, is throttled by the expansion valve, absorbs heat by the evaporator, and repeats the cycle of being sucked into the first rotary compression element of the rotary compressor.

  The high-pressure refrigerant discharged into the compression chamber of the second rotary compression element passes through an introduction path provided from the compression chamber of the second rotary compression element to the back surface of the vane, and is installed on the back surface of the vane. Entering the pressure chamber, the back pressure chamber of the vane is filled with the second-stage discharge pressure. Thereby, the vane provided in the 2nd rotation compression element was made to act as a force which pushes later. That is, the conventional rotary compressor is configured to press the vane against the roller by using the discharge pressure to the second rotary compression element as the back pressure of the vane, and even if the pressure in the compression chamber of the second rotary compression element becomes high. The vane was designed to have enough back pressure to counteract that force.

  The vane attached to such a rotary compressor is inserted into a guide groove provided in the radial direction of the cylinder so as to be movable in the radial direction of the cylinder. Since this vane needs to be pressed against the roller side, a structure is conventionally used to press the vane against the roller by the biasing force of the spring and the back pressure from the back pressure chamber. In the rotary compression element 2, the pressure in the cylinder is higher than the intermediate pressure in the sealed container, so the pressure in the sealed container cannot be used as the back pressure of the vane, and the vane is urged to the roller side. Troubles. In addition, the lower support member needs to be processed such as a discharge silencer chamber and a communication path with the sealed container, which increases the cost.

  The present invention has been made in order to solve the problems of the related art, and has a structure in which back pressure can be applied to the vanes of the second rotary compression element without hindrance, so that the processing can be simplified. An object of the present invention is to provide a pressure type multistage compression type rotary compressor.

That is, in the rotary compressor of the present invention, an electric element and first and second rotary compression elements driven by the electric element are provided in a hermetic container, and gas compressed by the first rotary compression element is supplied. In a rotary compressor that discharges the gas into the hermetic container and further compresses the discharged intermediate-pressure gas by the second rotary compression element, a cylinder for constituting the second rotary compression element and the electric element A roller that is fitted in an eccentric portion formed on the rotation shaft and rotates eccentrically in the cylinder, a closing member that closes the opening surface of the cylinder, a low pressure chamber side and a high pressure inside the cylinder in contact with the roller A vane partitioned into a chamber side, a back pressure chamber for applying a back pressure to the vane, and a back pressure passage formed in the closing member and communicating the high pressure chamber side in the cylinder and the back pressure chamber. equipped, under A sintered material of iron in the support member, the high-pressure chamber side opening of the back pressure passage is characterized by being opened and closed by the roller by the rotational position of the rollers.

The rotary compressor according to a second aspect of the invention is characterized in that, in the first aspect of the invention, the opening of the back pressure passage is opened when the rotational position of the roller is in the range of 90 ° to 300 °.

  Thus, according to the present invention, it is possible to improve operational efficiency, durability, input reduction, and the like while simplifying the structure of the rotary compressor.

  Next, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view of an internal intermediate pressure type multi-stage (two-stage) rotary rotary compressor 10 having first and second rotary compression elements 32 and 34 as an embodiment of the rotary compressor of the present invention. Fig. 3 is a front view of the rotary compressor 10, Fig. 3 is a side view of the rotary compressor 10, Fig. 4 is another longitudinal sectional view of the rotary compressor 10, Fig. 5 is yet another longitudinal sectional view of the rotary compressor 10, and Fig. 6 is a rotary compressor. FIG. 7 is an enlarged sectional view of the rotary compression mechanism portion 18 of the rotary compressor 10.

  In each figure, reference numeral 10 denotes an internal intermediate pressure multistage compression rotary compressor that uses carbon dioxide (CO2) as a refrigerant. The rotary compressor 10 includes a cylindrical sealed container 12 made of a steel plate and an internal space of the sealed container 12. Of the electric element 14 disposed on the upper side of the electric element 14 and the first rotary compression element 32 (first stage) and the second rotation which are arranged below the electric element 14 and are driven by the rotating shaft 16 of the electric element 14. The rotary compression mechanism 18 is composed of a compression element 34 (second stage).

  The height dimension of the rotary compressor 10 of the embodiment is 220 mm (outer diameter 120 mm), the height dimension of the electric element 14 is about 80 mm (outer diameter 110 mm), and the height dimension of the rotary compression mechanism 18 is about 70 mm (outside). The distance between the electric element 14 and the rotary compression mechanism 18 is about 5 mm. Further, the excluded volume of the second rotary compression element 34 is set smaller than the excluded volume of the first rotary compression element 32.

  In the embodiment, the sealed container 12 is made of a steel plate having a thickness of 4.5 mm, the bottom is an oil reservoir, the container body 12A that houses the electric element 14 and the rotary compression mechanism 18, and the upper opening of the container body 12A is closed. And a circular mounting hole 12D is formed in the center of the upper surface of the end cap 12B. The mounting element 12D has a power supply to the electric element 14. A terminal (wiring is omitted) 20 is attached.

  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 and 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.

  The electric element 14 includes a stator 22 attached in an annular shape along the inner peripheral surface of the upper space of the hermetic container 12, and a rotor 24 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.

  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. 6). Similarly to the stator 22, the rotor 24 is also formed by a laminated body 30 of electromagnetic steel plates, and a permanent magnet MG is inserted into the laminated body 30.

  An intermediate partition plate 36 is sandwiched between the first rotary compression element 32 and the second rotary compression element 34. That is, the first rotary compression element 32 and the second rotary compression element 34 include an intermediate partition plate 36, a cylinder 38 and a cylinder 40 disposed above and below the intermediate partition plate 36, and the inside of the upper and lower cylinders 38 and 40. The upper and lower rollers 46 and 48 are fitted to the upper and lower eccentric portions 42 and 44 provided on the rotating shaft 16 with a phase difference of 180 degrees and rotate eccentrically, and the upper and lower cylinders 38 are in contact with the upper and lower rollers 46 and 48. , 40 are divided into a low pressure chamber side and a high pressure chamber side, respectively, and upper and lower vanes 50 (lower vanes are not shown), an upper opening surface of the upper cylinder 38 and an opening surface of the lower cylinder 40 below. And an upper support member 54 and a lower support member 56 as a closing member that also serves as a bearing for the rotary shaft 16.

  The upper support member 54 and the lower support member 56 are formed with suction passages 58 and 60 that communicate with the inside of the upper and lower cylinders 38 and 40 through suction ports 161 and 162, and recessed discharge silencer chambers 62 and 64, respectively. The openings of both the discharge silencing chambers 62 and 64 are respectively closed by covers. That is, the discharge silence chamber 62 is closed by an upper cover 66 as a cover, and the discharge silence chamber 64 is closed by a lower cover 68 as a cover.

  In this case, a bearing 54A is erected at the center of the upper support member 54, and a cylindrical bush 122 is mounted on the inner surface of the bearing 54A. Further, a bearing 56A is formed through the center of the lower support member 56, and a cylindrical bush 123 is mounted on the inner surface of the bearing 56A. The bushes 122 and 123 are made of a material having good slidability as will be described later, and the rotating shaft 16 is connected to the bearing 54A of the upper support member 54 and the bearing 56A of the lower support member 56 through the bushes 122 and 123. Retained.

In this case, the lower cover 68 is constituted by a donut-shaped circular steel plate, and the four peripheral portions are fixed to the lower support member 56 from below by the main bolts 129... The lower surface opening of the discharge silencing chamber 64 communicating with the inside of the lower cylinder 40 of the compression element 32 is closed. The front ends of the main bolts 129 are screwed into the upper support member 54. The inner peripheral edge of the lower cover 68 protrudes inward from the inner surface of the bearing 56A of the lower support member 56, whereby the lower end surface of the bush 123 is held by the lower cover 68 and is prevented from falling off (FIG. 9). FIG.
Indicates a lower surface of the lower support member 56, and 128 is a discharge valve of the first rotary compression element 32 that opens and closes the discharge port 41 in the discharge silencer chamber 64.

  Here, the lower support member 56 is made of an iron-based sintered material (or can be cast), and the surface (lower surface) on which the lower cover 68 is attached is processed to have a flatness of 0.1 mm or less. Steam processing has been added. Since the surface on which the lower cover 68 is attached by this steam treatment is made of iron oxide, the hole inside the sintered material is blocked and the sealing performance is improved. This eliminates the need for a gasket between the lower cover 68 and the lower support member 56.

  In addition, the electric element 14 side of the upper cover 66 in the discharge silencer chamber 64 and the sealed container 12 is communicated with a communication passage 63 that is a hole penetrating the upper and lower cylinders 38 and 40 and the intermediate partition plate 36 (FIG. 4). ). In this case, an intermediate discharge pipe 121 is erected at the upper end of the communication path 63, and this intermediate discharge pipe 121 is between the adjacent stator coils 28, 28 wound around the stator 22 of the upper electric element 14. It is directed to the gap (FIG. 6).

  Further, the upper cover 66 closes the upper opening of the discharge silencer chamber 62 communicating with the inside of the upper cylinder 38 of the second rotary compression element 34 at the discharge port 39, and the discharge silencer chamber 62 and the electric element inside the sealed container 12. Divide into 14 sides. As shown in FIG. 11, the upper cover 66 has a thickness of 2 mm or more and 10 mm or less (6 mm is the most desirable in the embodiment), and a substantially donut having a hole through which the bearing 54A of the upper support member 54 is formed. In the state where a beaded gasket 124 (FIG. 12) is sandwiched between the upper support member 54 and the upper support member 54, the peripheral portion has four main bolts 78. The upper support member 54 is fixed from above. The front ends of the main bolts 78 are screwed into the lower support member 56.

  By setting the upper cover 66 to have such a thickness dimension, it is possible to achieve downsizing and secure an insulation distance from the electric element 14 while sufficiently withstanding the pressure of the discharge silencer chamber 62 that is higher than that in the sealed container 12. You can also do that. Further, an O-ring 126 is provided between the inner peripheral edge of the upper cover 66 and the outer surface of the bearing 54A (FIG. 12). By sealing the bearing 54A side with the O-ring 126, it is possible to sufficiently seal the inner periphery of the upper cover 66 and prevent gas leakage, and the volume of the discharge silencer chamber 62 can be increased. The ring eliminates the need to fix the inner peripheral edge of the upper cover 66 to the bearing 54A.

  Here, in FIG. 11, 127 is a discharge valve of the second rotary compression element 34 that opens and closes the discharge port 39 in the discharge silencer chamber 62.

  Next, in the intermediate partition plate 36 that closes the lower opening surface of the upper cylinder 38 and the upper opening surface of the lower cylinder 40, a position corresponding to the suction side in the upper cylinder 38 is shown in FIGS. 13 and 14. As shown in FIG. 1, a through hole 131 is formed from the outer peripheral surface to the inner peripheral surface, and the outer peripheral surface communicates with the inner peripheral surface to form an oil supply passage. A sealing material on the outer peripheral surface side of the through hole 131 is formed. 132 is press-fitted to seal the opening on the outer peripheral surface side. A communication hole 133 extending upward is formed in the middle of the through hole 131.

  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 161 (suction side) of the upper cylinder 38 (FIG. 15). Further, in the rotating shaft 16, as shown in FIG. 7, a vertical oil hole 80 at the center of the shaft and lateral oil supply holes 82 and 84 communicating with the oil hole 80 (upper and lower eccentric portions 42 and 44 of the rotating shaft 16). The opening on the inner peripheral surface side of the through hole 131 of the intermediate partition plate 36 communicates with the oil hole 80 via these oil supply holes 82 and 84.

  As will be described later, since the inside of the sealed container 12 is at an intermediate pressure, it is difficult to supply oil into the upper cylinder 38, which is at a high pressure in the second stage. The oil that has been pumped up from the oil sump at the bottom of 12 and raised through the oil hole 80 enters the through hole 131 of the intermediate partition plate 36 and passes through the communication holes 133 and 134 to the upper cylinder 38. It is supplied to the suction side (suction port 161).

  In FIG. 16, L indicates the pressure fluctuation on the suction side of the upper cylinder 38, and P1 in the drawing indicates the pressure on the inner peripheral surface of the intermediate partition plate 36. As indicated by L1 in this figure, the suction side pressure (suction pressure) of the upper cylinder 38 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 from the through hole 131 and the communication hole 133 of the intermediate partition plate 36 to the upper cylinder 38 through the communication hole 134 of the upper cylinder 38.

  As described above, the upper and lower cylinders 38 and 40, the intermediate partition plate 36, the upper and lower support members 54 and 56, and the upper and lower covers 66 and 68 are fastened from above and below by the four main bolts 78. However, the upper and lower cylinders 38, 40, the intermediate partition plate 36, and the upper and lower support members 54, 56 are fastened by auxiliary bolts 136, 136 positioned outside the main bolts 78, 129 (FIG. 4). The auxiliary bolt 136 is inserted from the upper support member 54 side, and the tip thereof is screwed to the lower support member 56.

  The auxiliary bolt 136 is positioned in the vicinity of the guide groove 70 described later of the vane 50 described later. Thus, by adding the auxiliary bolts 136 and 136 and integrating the rotary compression mechanism 18, the sealing performance against the extremely high pressure inside is ensured, and the vicinity of the guide groove 70 of the vane 50. Therefore, it is possible to prevent inconvenience that a high back pressure applied to the vane 50 from the back pressure chamber 74 described later leaks.

  On the other hand, a guide groove 70 for storing the vane 50 described above and a storage portion 70A for storing a spring 76 as a spring member located outside the guide groove 70 are formed in the upper cylinder 38. The portion 70A is open to the guide groove 70 side and the closed container 12 (container body 12A) side (FIG. 8). The spring 76 is in contact with the outer end of the vane 50 and constantly urges the vane 50 toward the roller 46. 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.

  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 upper cylinder 38, that is, the outer end of the storage portion 70A, and the container body 12A of the sealed container 12 is smaller than the distance from the O-ring 138 to the end of the plug 137 on the sealed container 12 side. Is set. Due to such a dimensional relationship, as in the case where the plug 137 is press-fitted and fixed in the housing portion 70A, the upper cylinder 38 is deformed and the sealing performance with the upper support member 54 is deteriorated, resulting in a deterioration in performance. Can be avoided in advance.

  Even when the outer dimension of the plug 137 is set to be smaller than the inner dimension of the storage portion 70A and the plug 137 is fitted into the storage portion 70A with a gap, the distance between the upper cylinder 38 and the sealed container 12 can be reduced from the O-ring 138. Since the distance to the end of the plug 137 on the closed container 12 side is set to be smaller, even if the plug 137 moves in the direction in which it is pushed out of the storage portion 70A due to the high pressure on the spring 76 side (back pressure of the vane 50). Since the O-ring 138 is still positioned and sealed in the storage portion 70A when the movement is prevented by contacting the sealed container 12, there is no problem with the function of the plug 137.

On the other hand, on the opposite side of the guide groove 70 in the upper cylinder 38 from the roller 46, the above-described back pressure chamber 74 for applying a back pressure for urging the vane 50 to the roller 46 is formed. Yes. The back pressure chamber 74 has a substantially cylindrical shape extending between the intermediate partition plate 36 and the upper support member 54 and is formed so as to penetrate into the upper cylinder 38 (FIG. 19). The back pressure chamber 74 communicates with the storage portion 70A and the guide groove 70, and a gas on the high pressure chamber side in the upper cylinder 38 flows into the back pressure chamber 74 from a back pressure passage 72, which will be described later. Back pressure is applied from behind the vane 50 to urge the vane 50 toward the roller 46.

  The back pressure passage 72 is formed in the upper support member 54 (blocking member). One end of the back pressure passage 72 opens into the upper cylinder 38 through an opening 72A formed in the lower surface of the upper support member 54 at a position corresponding to the high pressure chamber side in the upper cylinder 38, and the other end enters the back pressure chamber 74. An opening is made on the lower surface of the upper support member 54 at a corresponding position (see FIG. 20), and the high pressure chamber side in the upper cylinder 38 and the back pressure chamber 74 are communicated. The pressure on the high pressure chamber side in the cylinder 38 is supplied to the back pressure chamber 74 through the back pressure passage 72. The opening on the high pressure chamber side of the back pressure passage 72 is within a predetermined range before and after the rotation position (180 °) of the roller 46 when the rotation position of the roller 46 when the vane 50 protrudes most is 180 °. In the rotational position, the roller 46 opens the opening 72 </ b> A of the back pressure passage 72.

  In this case, in the embodiment, when the rotational position of the roller 46 is a predetermined range before and after 180 ° (position (C) in FIG. 19), the rotational position of the roller 46 is in the range of 90 ° to 300 °. The opening 72A is arranged so that the opening 72A is opened. That is, the opening 72A is opened at the position where the roller 46 is rotated and the rotational position is 90 ° (FIG. 19F), and is closed at the position where the roller 46 is 300 ° (FIG. 19B). . Accordingly, the pressure on the high pressure chamber side in the upper cylinder 38 is supplied to the back pressure chamber 74 through the back pressure passage 72 at the rotational position of 90 ° to 300 °.

  As a result, the refrigerant gas on the high pressure chamber side in the upper cylinder 38 flows into the back pressure chamber 74 and back pressure is applied to the vane 50, so that the vane 50 can be biased toward the roller 46.

  By the way, the connecting portion 90 that connects the upper and lower eccentric portions 42 and 44 formed integrally with the rotating shaft 16 with a phase difference of 180 degrees has a cross-sectional shape that is larger than the circular cross section of the rotating shaft 16. In order to enlarge and give rigidity, it is made into a non-circular shape such as a rugby ball (FIG. 17). That is, the cross-sectional shape of the connecting portion 90 that connects the upper and lower eccentric portions 42 and 44 provided on the rotating shaft 16 is increased in thickness in the direction perpendicular to the eccentric direction of the upper and lower eccentric portions 42 and 44 (hatching in the figure). Part).

  As a result, the cross-sectional area of the connecting portion 90 that connects the upper and lower eccentric portions 42 and 44 provided integrally with the rotating shaft 16 is increased, the second moment is increased, and the strength (rigidity) is increased. Improves sex. In particular, when a refrigerant having a high working pressure is compressed in two stages, the load applied to the rotary shaft 16 increases due to the large pressure difference between the high and low pressures. However, the strength (rigidity) is increased by increasing the cross-sectional area of the connecting portion 90. The rotation shaft 16 is prevented from being elastically deformed.

  In this case, if the center of the upper eccentric portion 42 is O1, and the center of the lower 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 rotary shaft 16 is chucked to the cutting machine to cut the upper and lower eccentric portions 42 and 44 and the connecting portion 90, after machining the eccentric portion 42, only the radius is changed and one surface of the connecting portion 90 is changed. It is possible to perform an operation of machining, changing the chuck position, machining the other surface of the connecting portion 90, and machining the eccentric portion 44 by changing only the radius. As a result, the number of times of rechucking the rotating shaft 16 is reduced and the productivity is remarkably improved.

  In this case, the refrigerant is environmentally friendly, uses carbon dioxide (CO2) as an example of carbon dioxide, which is a natural refrigerant in consideration of flammability and toxicity, and the oil as the lubricating oil is, for example, a mineral Existing oils such as oil (mineral oil), alkylbenzene oil, ether oil and ester oil are used.

  On the side surface of the container main body 12A of the sealed container 12, the suction passages 58, 60 of the upper support member 54 and the lower support member 56, the upper side of the discharge silencer chamber 62, and the upper cover 66 (position substantially corresponding to the lower end of the electric element 14). The sleeves 141, 142, 143, and 144 are fixed by welding at positions corresponding to. The sleeves 141 and 142 are adjacent to each other vertically, and the sleeve 143 is substantially diagonal to the sleeve 141. Further, the sleeve 144 is located at a position shifted by approximately 90 degrees from the sleeve 141.

  One end of a refrigerant introduction pipe 92 for introducing refrigerant gas into the upper cylinder 38 is inserted and connected into the sleeve 141, and one end of the refrigerant introduction pipe 92 is communicated with the suction passage 58 of the upper cylinder 38. The refrigerant introduction pipe 92 passes through the upper side of the sealed container 12 to reach the sleeve 144, and the other end is inserted and connected into the sleeve 144 to communicate with the sealed container 12.

  Also, one end of a refrigerant introduction pipe 94 for introducing refrigerant gas into the lower cylinder 40 is inserted and connected in the sleeve 142, and one end of the refrigerant introduction pipe 94 is communicated with the suction passage 60 of the lower cylinder 40. The other end of the refrigerant introduction tube 94 is connected to the lower end of the accumulator 146. Further, a refrigerant discharge pipe 96 is inserted and connected into the sleeve 143, and one end of the refrigerant discharge pipe 96 is communicated with the discharge silencer chamber 62.

  The accumulator 146 is a tank that performs gas-liquid separation of the suction refrigerant, and is attached to a bracket 147 on the hermetic container side welded to the upper side surface of the container body 12A of the hermetic container 12 via a bracket 148 on the accumulator side. . The bracket 148 extends upward from the bracket 147 and holds a substantially central portion of the accumulator 146 in the vertical direction. In this state, the accumulator 146 is arranged along the side of the sealed container 12.

  The refrigerant introduction pipe 92 rises after exiting from the sleeve 141, bent in the right direction in the embodiment, and then rises, and the lower end of the accumulator 146 becomes close to the refrigerant introduction pipe 92. Therefore, the refrigerant introduction pipe 94 descending from the lower end of the accumulator 146 is routed around the left side opposite to the bending direction of the refrigerant introduction pipe 92 as viewed from the sleeve 141 so as to reach the sleeve 142 (FIG. 3). ).

  That is, the refrigerant introduction pipes 92 and 94 respectively communicating with the suction passages 58 and 60 of the upper support member 54 and the lower support member 56 are bent in opposite directions in the horizontal direction when viewed from the sealed container 12. Thereby, even if the vertical dimension of the accumulator 146 is enlarged to increase the volume, consideration is given so that the refrigerant introduction pipes 92 and 94 do not interfere with each other.

  Further, a flange 151 that can be engaged with a coupler for pipe connection is formed around the outer surfaces of the sleeves 141, 143, and 144, and a thread groove 152 for pipe connection is formed on the inner surface of the sleeve 142. . As a result, the sleeves 141, 143, and 144 can be easily connected to the flanges 151 of the test pipe couplers when the airtight test is performed in the final inspection in the manufacturing process of the rotary compressor 10. It becomes possible to easily screw the test pipe using the screw groove 152. In particular, the sleeves 141 and 142 that are adjacent in the vertical direction are formed with a flange 151 on one sleeve 141 and a thread groove 152 on the other sleeve 142, so that the test pipes can be connected to the sleeves 141 and 142 in a narrow space. Can be connected.

  And the rotary compressor 10 of an Example is used for the refrigerant circuit of the hot-water supply apparatus 153 as shown in FIG. That is, the refrigerant discharge pipe 96 of the rotary compressor 10 is connected to the inlet of the gas cooler 154 for water heating. This gas cooler 154 is provided in a hot water storage tank (not shown) of the hot water supply device 153. The pipe exiting the gas cooler 154 reaches the inlet of the evaporator 157 through an expansion valve 156 as a decompression device, and the outlet of the evaporator 157 is connected to the refrigerant introduction pipe 94. Further, although not shown in FIGS. 2 and 3, a defrost pipe 158 constituting a defrosting circuit branches off from the middle of the refrigerant introduction pipe 92, and the gas cooler 154 is connected via an electromagnetic valve 159 as a flow path control device. It is connected to a refrigerant discharge pipe 96 that reaches the inlet. In FIG. 18, the accumulator 146 is omitted.

  Next, the operation of the above configuration will be described. In the heating operation, the solenoid valve 159 is closed. When the stator coil 28 of the electric element 14 is energized through the terminal 20 and a wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. By this rotation, the upper and lower rollers 46 and 48 fitted to the upper and lower eccentric portions 42 and 44 provided integrally with the rotary shaft 16 rotate eccentrically in the upper and lower cylinders 38 and 40.

  Thus, the low pressure (first stage suction pressure LP: 4 MPaG) sucked from the suction port 162 to the low pressure chamber side of the lower cylinder 40 through the refrigerant introduction pipe 94 and the suction passage 60 formed in the lower support member 56. The refrigerant gas is compressed by the operation of the roller 48 and the vane to become an intermediate pressure (MP1: 8 MPaG), and from the high pressure chamber side of the lower cylinder 40 to the discharge port 41 and the discharge silencer chamber 64 formed in the lower support member 56, the communication path 63. Then, the liquid is discharged from the intermediate discharge pipe 121 into the sealed container 12.

  At this time, since the intermediate discharge pipe 121 is directed to the gap between the adjacent stator coils 28 and 28 wound around the stator 22 of the upper electric element 14, the refrigerant gas still having a relatively low temperature is supplied to the electric element. It becomes possible to actively supply in the 14 directions, and the temperature rise of the electric element 14 is suppressed. Moreover, the inside of the airtight container 12 becomes intermediate pressure (MP1) by this.

  Then, the intermediate pressure refrigerant gas in the sealed container 12 exits from the sleeve 144 (intermediate discharge pressure is MP1), and the suction port 161 passes through the refrigerant introduction pipe 92 and the suction passage 58 formed in the upper support member 54. To the low pressure chamber side of the upper cylinder 38 (second-stage suction pressure MP2). The sucked intermediate pressure refrigerant gas is compressed in the second stage by the operation of the roller 46 and the vane 50, but the opening 72A of the back pressure passage 72 is within the range of 90 ° or more and 300 ° or less. Is configured to open, and a suitable back pressure can be applied to the vane 50, so that the vane 50 can be operated smoothly. The suctioned intermediate pressure refrigerant gas is compressed by the second stage by the operation of the roller 46 and the vane 50 to become a high temperature and high pressure refrigerant gas (second stage discharge pressure HP: 12 MPaG), and from the high pressure chamber side. The gas flows into the gas cooler 154 through the discharge port 39 and the discharge silencer chamber 62 formed in the upper support member 54 and the refrigerant discharge pipe 96. The refrigerant temperature at this time has risen to approximately + 100 ° C., and the high-temperature and high-pressure refrigerant gas dissipates heat to heat the water in the hot water storage tank and generate hot water of about + 90 ° C.

  In the second-stage compression in the upper cylinder 38 described above, the refrigerant gas suction initial stage where the rotation angle position of the roller 46 starts from 0 ° is equal to the suction pressure (MP1) on the high-pressure chamber side in the upper cylinder 38 as well. is there. Therefore, when this refrigerant gas flows into the back pressure chamber 74, it is re-expanded and the compression efficiency is lowered. Further, a function as a back pressure for urging the vane 50 toward the roller 46 cannot be expected.

  On the other hand, in the final compression stage of the refrigerant gas in which the rotational angle position of the roller 46 is directed to 360 °, the high-pressure chamber side becomes the above-described extremely high high-pressure HP, so when such extremely high-pressure refrigerant gas flows into the back pressure chamber 74, The force for pressing the vane 50 against the roller 46 due to the back pressure becomes excessive, and on the contrary, the amount of work for pushing the vane 50 toward the guide groove 70 increases, and the input (electric power) increases, thereby reducing the efficiency.

  However, in the present invention, as described above, the roller 46 opens the opening 72A of the back pressure passage 72 only in the range where the rotational position of the roller 46 is 90 ° or more and 300 ° or less, and the high pressure chamber side and the back pressure chamber 74 are communicated. At the same time, since the opening 72A is closed so as not to communicate in the initial stage of suction in the range of 0 ° to 90 ° and the final stage of compression of 300 ° to 360 °, such efficiency deterioration can be prevented. Moreover, since the back pressure excess which presses the vane 50 against the roller 46 can be prevented, both durability is improved and the lubrication characteristics are also improved.

  On the other hand, the refrigerant itself is cooled in the gas cooler 154 and exits the gas cooler 154. Then, after the pressure is reduced by the expansion valve 156, the refrigerant flows into the evaporator 157 to evaporate, and is sucked into the first rotary compression element 32 from the refrigerant introduction pipe 94 through the accumulator 146 (not shown in FIG. 18). repeat.

  In particular, in an environment of low outside air temperature, frost forms on the evaporator 157 by such heating operation. In that case, the electromagnetic valve 159 is opened, the expansion valve 156 is fully opened, and the defrosting operation of the evaporator 157 is executed. As a result, the intermediate-pressure refrigerant in the sealed container 12 (including a small amount of high-pressure refrigerant discharged from the second rotary compression element 34) reaches the gas cooler 154 through the defrost pipe 158. The temperature of this refrigerant is about +50 to + 60 ° C., and the gas cooler 154 does not radiate heat, but initially the refrigerant absorbs heat. Then, the refrigerant discharged from the gas cooler 154 passes through the expansion valve 156 and reaches the evaporator 157. That is, the refrigerant having a relatively high intermediate pressure is supplied directly to the evaporator 157 without being depressurized, whereby the evaporator 157 is heated and defrosted.

  Here, when the high-pressure refrigerant discharged from the second rotary compression element 34 is supplied to the evaporator 157 without depressurization and defrosted, the first rotary compression element 32 is opened to fully open the expansion valve 156. As a result, the suction pressure of the first rotary compression element 32 increases (the intermediate pressure). Although this refrigerant is discharged through the second rotary compression element 34, the discharge pressure of the second rotary compression element 34 is the same as the suction pressure of the first rotary compression element 32 because the expansion valve 156 is fully open. As a result, a pressure reversal phenomenon occurs between the discharge (high pressure) and the suction (intermediate pressure) of the second rotary compression element 34. However, since the intermediate-pressure refrigerant gas discharged from the first rotary compression element 32 is taken out from the sealed container 12 as described above and the evaporator 157 is defrosted, the high pressure and the intermediate pressure are reversed. Can be prevented.

  In this way, the back pressure passage 72 that connects the high pressure chamber side in the upper cylinder 38 and the back pressure chamber 74 is formed in the upper support member 54, so that the high pressure in the cylinder 38 is connected via the back pressure passage 72. The chamber pressure can be supplied to the back pressure chamber 74. Thereby, in the rotary compressor 10 in which the inside of the sealed container 12 has an intermediate pressure, it is possible to apply a back pressure for urging the vane 50 toward the roller 46 without any trouble. In particular, since the back pressure passage 72 is simply formed in the upper support member 54, the back pressure passage 72 can be processed extremely easily, and the workability of the back pressure passage 72 is greatly improved. Will be able to.

  In the above embodiment, the back pressure passage 72 for connecting the high pressure chamber side in the upper cylinder 38 and the back pressure chamber 74 is provided in the upper support member 54. However, the back pressure passage 72 is not limited to this. The present invention is effective even if it is provided on the partition plate 36 (which serves as a closing member in the present invention).

  Although carbon dioxide (CO 2) is used as the refrigerant in the rotary compressor 10, the present invention is not limited to this refrigerant, and the present invention is effective when other natural refrigerants such as hydrocarbon (HC) and ammonia (NH 3) are used. .

It is a longitudinal cross-sectional view of the rotary compressor of the Example of this invention. It is a front view of the rotary compressor of FIG. It is a side view of the rotary compressor of FIG. It is another longitudinal cross-sectional view of the rotary compressor of FIG. FIG. 3 is still another longitudinal sectional view of the rotary compressor of FIG. 1. It is a plane sectional view of the electric element part of the rotary compressor of FIG. It is an expanded sectional view of the rotary compression mechanism part of the rotary compressor of FIG. It is an expanded sectional view of the vane part of the 2nd rotary compression element of the rotary compressor of FIG. It is sectional drawing of the lower support member and lower cover of the rotary compressor of FIG. It is a bottom view of the lower support member of the rotary compressor of FIG. FIG. 2 is a top view of an upper support member and an upper cover of the rotary compressor in FIG. 1. It is sectional drawing of the upper support member and upper cover of the rotary compressor of FIG. It is a top view of the intermediate partition plate of the rotary compressor of FIG. FIG. 13A is a cross-sectional view taken along line AA. It is a top view of the upper cylinder of the rotary compressor of FIG. It is a figure which shows the pressure fluctuation of the suction side of the upper cylinder of the rotary compressor of FIG. It is sectional drawing for demonstrating the shape of the connection part of the rotating shaft of the rotary compressor of FIG. It is a refrigerant circuit figure of the hot water supply apparatus to which the rotary compressor of FIG. 1 is applied. It is a figure explaining the back pressure channel | path of the upper cylinder of the rotary compressor of FIG. It is a side view of the rotary compression mechanism part for showing the back pressure channel | path of the rotary compressor of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Rotary compressor 12 Airtight container 14 Electric element 16 Rotating shaft 18 Rotation compression mechanism part 20 Terminal 32 1st rotation compression element 34 2nd rotation compression element 36 Intermediate | middle partition plate 38, 40 Cylinder 39, 41 Discharge port 42 Eccentric part 44 Eccentric portion 46 Roller 48 Roller 50 Vane 54 Upper support member 56 Lower support member 62 Discharge silencer chamber 64 Discharge silencer chamber 66 Upper cover 68 Lower cover 70 Guide groove 70A Storage portion 72 Back pressure passage 72A Opening 74 Back pressure chamber 76 Spring 78, 129 Main bolt 90 Connecting part 132 Sealing material 137 Plug 138 O-ring

Claims (2)

An electric element and a first and a second rotary compression element driven by the electric element are provided in the sealed container, and the gas compressed by the first rotary compression element is discharged into the sealed container. In the rotary compressor that compresses the discharged intermediate-pressure gas by the second rotary compression element, a cylinder for constituting the second rotary compression element and an eccentric part formed on the rotary shaft of the electric element A roller that is fitted and eccentrically rotates in the cylinder, a closing member that closes the opening surface of the cylinder, a vane that contacts the roller and divides the cylinder into a low pressure chamber side and a high pressure chamber side, A back pressure chamber for applying a back pressure to the vane; and a back pressure passage formed in the closing member and communicating with the high pressure chamber side in the cylinder and the back pressure chamber. using a sintered material, the back Wherein the high pressure chamber side opening of the passage, the rotary compressor characterized in that it is opened and closed by the roller by the rotational position of the rollers. 2. The rotary compressor according to claim 1 , wherein the opening of the back pressure passage is opened when the rotational position of the roller is in a range of 90 ° to 300 ° .