JP2014190271A - Rotary compressor and air conditioner outdoor unit including the same - Google Patents

Abstract

A rotary compressor capable of cooling refrigeration oil O without consuming refrigeration capacity and an outdoor unit of an air conditioner equipped with the rotary compressor are provided.
An airtight container 2, an electric motor 4 accommodated in the airtight container, a compression mechanism section 3 driven by the electric motor, and a refrigerating machine oil O10 are provided.
Further, the lower end openings of the vane back chambers 13a and 13b communicating with the vane grooves 11a and 11b are closed by the connecting lid 15 having an opening, and the refrigerating machine oil O discharged from the opening of the connecting lid is discharged. A lead-out pipe 16 and a return pipe 18 of the cooling circuit that returns to the inside of the hermetic container after being led out of the hermetic container, and is used as power for circulating the refrigerating machine oil O in the cooling circuit, by reciprocating movement of the second vane 12b. Use the pumping action that occurs.
[Selection] Figure 1

Description

  Embodiments described herein relate generally to a rotary compressor used in a refrigeration cycle and an outdoor unit of an air conditioner including the rotary compressor.

  Conventionally, in this type of rotary compressor, a gas cooler system is known as a cooling means for cooling the refrigerating machine oil in the hermetic container. This gas cooler system is a system that cools refrigerating machine oil by circulating a part of a low-temperature gas refrigerant flowing through a refrigeration cycle inside a sealed container.

  However, in this gas cooler system, a part of the low-temperature gas refrigerant flowing through the refrigeration cycle is circulated inside the sealed container, so that a part of the refrigeration capacity in the refrigeration cycle is consumed for cooling the refrigerator oil. Therefore, there is a problem that the efficiency of the entire refrigeration system is reduced.

  The problem to be solved by the present invention is to provide a rotary compressor capable of cooling refrigeration oil without consuming refrigeration capacity, and an outdoor unit of an air conditioner equipped with the rotary compressor.

  The rotary compressor according to the embodiment includes an airtight container, an electric motor accommodated in the airtight container, a compression mechanism section driven by the electric motor, and refrigeration oil.

  The compression mechanism section closes the lower end opening of the vane back chamber communicating with the vane groove with a lid member having an opening, and guides the refrigerating machine oil discharged from the opening of the lid member to the outside of the sealed container. After that, a cooling circuit for returning to the inside of the sealed container is provided, and a pump action generated by the reciprocating motion of the vane is used as power for circulating the refrigerating machine oil in the cooling circuit.

The fragmentary longitudinal cross-section which shows a part of rotary compressor which concerns on 1st Embodiment with a longitudinal cross-section. The principal part enlarged view of the II section of FIG. The principal part enlarged view of the rotary compressor which concerns on 2nd Embodiment. The fragmentary longitudinal cross-section which shows a part of rotary compressor which concerns on 3rd Embodiment in a longitudinal cross-section. The principal part enlarged view of the rotary compressor which concerns on 4th Embodiment. The fragmentary longitudinal cross-section of the rotary compressor which concerns on 5th Embodiment. The plane schematic diagram which shows the whole structure of the outdoor unit which concerns on 6th Embodiment.

  Hereinafter, a rotary compressor according to an embodiment and an outdoor unit including the rotary compressor will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the same or an equivalent part in several drawing.

(First embodiment)
As shown in FIG. 1, the rotary compressor 1 has a sealed container 2, and refrigeration oil O is accommodated in the sealed container 2. In addition, a compression mechanism unit 3 is provided in the lower part of the sealed container 2 and an electric motor 4 is provided in the upper part. The compression mechanism unit 3 and the electric motor 4 are connected by a rotating shaft 5.

  The electric motor 4 is fixed to the inner peripheral surface of the hermetic container 2 by press-fitting or shrink fitting, and has a cylindrical stator 4a on which windings are mounted, and a rotor provided rotatably inside the stator 4a. 4b.

  The compression mechanism section 3 includes a first cylinder 7A on the upper surface portion of the intermediate partition plate 6 via the intermediate partition plate 6 and a second cylinder 7B on the lower surface portion. Further, the main bearing 8 is attached and fixed to the upper surface of the first cylinder 7A, and the auxiliary bearing 9 is attached and fixed to the lower surface of the second cylinder 7B.

  The main bearing 8 supports the main shaft portion 5 a of the rotating shaft 5, and the auxiliary bearing 9 supports the auxiliary shaft portion 5 b of the rotating shaft 5. The rotating shaft 5 penetrates through the insides of the first and second cylinders 7A and 7B, and integrally includes a first eccentric part a and a second eccentric part b formed with a phase difference of about 180 °. Yes.

  The first and second eccentric parts a and b have the same diameter as each other, and are assembled so as to be positioned at the inner diameter parts of the first and second cylinders 7A and 7B. The first eccentric roller 10a is fitted to the circumferential surface of the first eccentric part a, and the second eccentric roller 10b is fitted to the circumferential surface of the second eccentric part b.

  The inner diameter portion of the first cylinder 7A is surrounded by the main bearing 8 and the intermediate partition plate 6, and a first cylinder chamber Sa is formed. An inner diameter portion of the second cylinder 7B is surrounded by the auxiliary bearing 9 and the intermediate partition plate 6, and a second cylinder chamber Sb is formed.

  The cylinder chambers Sa and Sb are formed to have the same diameter and height, and in the cylinder chambers Sa and Sb, the eccentric rollers 10a and 10b are partly peripheral walls and part of the peripheral walls of the cylinder chambers Sa and Sb. It is accommodated so as to be eccentrically rotated while being in line contact.

  The first cylinder 7A is provided with a first vane groove 11a communicating with the first cylinder chamber Sa, and the first vane 12a is movably accommodated in the first vane groove 11a. Is done. The second cylinder 7B is provided with a second vane groove 11b communicating with the second cylinder chamber Sb, and the second vane 12b is movably accommodated in the second vane groove 11b. .

  The front ends of the vanes 12a and 12b are formed in a semicircular shape in a plan view, projecting into the opposing cylinder chambers Sa and Sb, and circular in the plan view, the first and second eccentric rollers 10a and 10b. Line contact can be made with the peripheral wall regardless of the rotation angle.

  A first vane back chamber 13a is provided on the side opposite to the cylinder chamber Sa of the first vane groove 11a of the first cylinder 7A, and the first vane back chamber 13a is a compression spring (not shown). A spring member is received. This spring member is interposed between the rear end side end face of the first vane 12a and the inner peripheral wall of the sealed container 2, and always forcibly contacts the first vane 12a to the first eccentric roller 10a side. Applying elastic force (back pressure) to press.

  A second vane back chamber 13b is provided on the side opposite to the cylinder chamber Sb of the second vane groove 11b of the second cylinder 7B, and a compression spring (not shown) is provided in the second vane back chamber 13b. A spring member is accommodated. This spring member is interposed between the rear end side end surface of the vane and the inner peripheral wall of the sealed container 2 and elastically presses the second vane 12b slidably in contact with the second eccentric roller 10b at all times. (Back pressure) is applied to the second vane 12b.

  The accumulator 14 includes a first suction refrigerant pipe Pa that passes through the side of the sealed container 2 and the first cylinder 7A and communicates directly with the first cylinder chamber Sa, and the sealed container 2 and the second cylinder. And a second suction refrigerant pipe Pb that passes through the 7B side and communicates directly with the second cylinder chamber Sb.

  Then, as shown in FIG. 2, a lid member is formed on one of the first and second vane back chambers 13a and 13b, for example, on the outer surface (lower surface) of the lower opening 13c that is the lower end opening of the second vane back chamber 13b. The connection lid 15 which is an example of the connection lid 15 is closed and closed, and the lead-out pipe 16 connected to the connection lid 15 is communicated with the lower opening 13c.

  The first and second vane back chambers 13a and 13b each have an upper opening 13d that opens at the upper end facing the lower opening 13c in the vertical direction on the upper end surface in the drawing. Since the liquid level of the refrigerating machine oil O accommodated in the hermetic container 2 reaches above the upper opening 13d of the first vane chamber 13a, the first and second vane back chambers 13a and 13b. Inside, the refrigerating machine oil O is always filled.

  As shown in FIG. 1, the leading end portion 16a of the outlet tube 16 penetrates the side wall of the sealed container 2 in a liquid-tight manner in the horizontal direction and extends to the outside of the sealed container 2 to be cooled by a fin tube heat exchanger. It is connected to an oil pipe inlet (not shown) of the vessel 17. For example, the oil pipe is formed in a serpentine shape that repeats a U-shaped meander several times, and is configured to vertically penetrate a plurality of fins arranged to face each other at a required pitch. A return pipe 18 is connected to the oil outlet. Is done.

  The distal end portion 18 a of the return pipe 18 penetrates the side wall of the sealed container 2 in a liquid-tight manner in the horizontal direction and extends to the oil reservoir at the bottom in the sealed container 2. Thereby, a cooling circuit for the refrigerating machine oil O is formed.

  Since the rotary compressor 1 according to the present embodiment is configured as described above, when the electric motor 4 is energized and the compression mechanism unit 3 is driven, the first of the first and second cylinders 7A and 7B. The first and second eccentric rollers 10a and 10b are eccentrically driven in the second cylinder chambers Sa and Sb, respectively.

  As a result, the refrigerant in the first and second cylinder chambers Sa and Sb is compressed, becomes a high-temperature and high-pressure gas refrigerant, is discharged into the sealed container 2, and is discharged from the discharge pipe 2a to a condenser (not shown). .

  On the other hand, according to the eccentric motion of the first and second eccentric rollers 10a and 10b, the first and second vanes 12a and 12b that are in sliding contact with the outer peripheral surfaces of the first and second eccentric rollers 10a and 10b. Reciprocate in the first and second vane grooves 11a and 11b and the first and second vane back chambers 13a and 13b, respectively.

  Therefore, a pumping action is generated in the first and second vane back chambers 13a and 13b shown in FIG. That is, the second vane back chamber 13b will be described. When the second vane 12b moves in the direction of the second cylinder chamber Sb, the pressure in the second vane back chamber 13b decreases, and the second vane back chamber 13b. Refrigerating machine oil O is sucked into the second vane back chamber 13b from the upper opening 13d of 13b. At this time, the refrigerating machine oil O in the outlet pipe 16 also flows back into the second vane back chamber 13b through the lower opening 13c, but the amount is very small because the passage resistance is large. Further, when the second vane 12b moves from the direction of the second cylinder chamber Sb to the second vane back chamber 13b, the pressure in the second vane back chamber 13b increases, and the second vane back chamber 13b increases. Refrigerating machine oil is discharged from the upper opening 13d and the lower opening 13c, respectively.

  By repeating such an operation, since the outlet pipe 16 is connected to the lower opening 13c, the refrigerating machine oil O is discharged into the outlet pipe 16 from the lower opening 13c.

  The refrigerating machine oil O discharged into the lead-out pipe 16 passes through the lead-out pipe 16 and flows into the cooler 17 of the finned tube heat exchanger disposed outside the sealed container 2, where heat is exchanged with the outside air. To be cooled.

  The refrigerating machine oil O cooled by the cooler 17 is returned to the oil sump in the sealed container 2 through the return pipe 18 again, for example. For this reason, the refrigerating machine oil O in the oil reservoir is cooled.

  This cooling effect of the refrigerating machine oil O exhibits a remarkable effect when HFC-32 is used as a refrigerant. That is, the HFC-32 refrigerant has a characteristic that the discharge temperature rises, for example, by about 20 ° C. as compared with conventional refrigerants R22 and R410A. Further, since the temperature of the refrigerating machine oil O during the operation of the compressor is proportional to the refrigerant discharge temperature, the temperature of the refrigerating machine oil O in the hermetic container 2 under the atmosphere of the HFC-32 refrigerant having a high discharge temperature also greatly increases.

  For this reason, since the viscosity of the refrigerating machine oil O itself falls, the lubricity of a compressor sliding part will deteriorate. Further, when the temperature of the refrigerating machine oil O is increased, there is a problem that the refrigerating machine oil O is deteriorated and the inherent lubrication performance is lowered.

  On the other hand, in this embodiment, since this refrigerator oil O is cooled, the said malfunction by the high temperature of the refrigerator oil O can be eliminated.

  According to the present embodiment, the refrigerating machine oil is generated by the pump action generated by the reciprocation of the second vane 12b that reciprocates in the second vane chamber 11b in accordance with the eccentric motion of the second eccentric roller 10b. Since O is circulated, it is not necessary to provide another drive source such as a pump for circulating the refrigerating machine oil O, and energy can be saved correspondingly.

(Second Embodiment)
FIG. 3 is an enlarged view of a main part of the rotary compressor 1 according to the second embodiment. As shown in FIG. 3, the second embodiment is characterized in that the shape of the inlet portion 16b of the outlet pipe 16 connected to the lower opening portion 13c of the second vane back chamber 13b is formed in a tapered shape. The other configuration is the same as that of the first embodiment.

  According to the second embodiment, the refrigeration pushed out from the lower opening portion 13c of the second vane back chamber 13b to the tapered inlet portion 16b of the outlet pipe 16 by the pump action by the reciprocating motion of the second vane 12b. The flow path resistance of the machine oil O can be reduced. For this reason, since the circulation flow rate of the refrigerating machine oil O circulating in the hermetic container 2 and the cooler 17 can be increased, the cooling efficiency of the refrigerating machine oil O can be improved.

(Third embodiment)
FIG. 4 is a partial longitudinal sectional view of the rotary compressor 1 according to the third embodiment. As shown in FIG. 4, the third embodiment is characterized in that a check valve 19 is interposed in the middle of the outlet pipe 16 extending to the outside of the sealed container 2. Is the same as in the first embodiment.

  According to the third embodiment, since the check valve 19 is provided in the middle of the lead-out pipe 16, the refrigerating machine oil O is discharged from the lead-out pipe 16 when the refrigerating machine oil O is sucked by the reciprocating operation of the second vane 12b. Backflow to the second vane back chamber 13b can be prevented.

(Fourth embodiment)
FIG. 5 is an enlarged view of a main part of the rotary compressor 1 according to the fourth embodiment.

  This fourth embodiment is characterized in that an ejector portion 20 is formed in the middle of the outlet pipe 16 in the refrigerating machine oil O in the sealed container 2. Other configurations are the same as those in the first embodiment.

  The ejector part 20 is divided into upper and lower parts in FIG. 5 to form an upper pipe 16b and a lower pipe 16c in the middle of the outlet pipe 16 where it is immersed in the refrigerator oil O. The lower pipe 16c is expanded in a funnel shape by expanding the upper opening end portion 16ca in FIG. 5 into a funnel shape having a diameter larger than the diameter of the opening end portion 16ba at the lower end of the upper tube 16b in the drawing and shrinking downward. It is formed in the diameter portion 16ca. Further, a lower opening end 16ba in the drawing of the upper tube 16b is inserted into the funnel-shaped enlarged portion 16ca, and the space between the outer peripheral surface of the insertion end 16ba and the inner peripheral surface of the funnel-shaped enlarged portion 16ca is inserted. Further, an annular opening 16cb is formed to constitute an ejector. The annular opening 16cb opens in the refrigerator oil O.

  Thereby, when the second vane 12b reciprocates in the second vane chamber 11a, the refrigerating machine oil O is sucked into the inside from the upper opening 13d of the second vane back chamber 13b by the pump action, From the lower opening 13c, it passes through the upper pipe 16b of the outlet pipe 16, and is discharged to the lower pipe 16c as shown by the arrow in FIG.

  Then, the refrigeration oil O around the annular opening 16cb is sucked into the annular opening 16cb due to the ejector effect of the funnel-shaped enlarged diameter portion 16ca, flows into the lower pipe 16c, and is transported to the cooler 17.

  Therefore, according to the fourth embodiment, the refrigerating machine oil O is circulated in the cooler 17 and the sealed container 2 by the pumping action of the second vane 12b and the ejector effect of the ejector part 20 of the outlet pipe 16. The circulation flow rate can be increased and the energy saving can be improved.

(Fifth embodiment)
FIG. 6 is an enlarged view of a main part of the rotary compressor 1 according to the fifth embodiment. The fifth embodiment is characterized in that an opening / closing valve 21 is interposed in the middle of the upper outlet pipe 16 extending to the outside of the sealed container 2, and other configurations are the same as in the first embodiment. It is.

  The on-off valve 21 is controlled to open / close or open according to a temperature detected by a temperature sensor (not shown) that detects the temperature of the refrigerating machine oil O or the discharge gas refrigerant in the sealed container 2.

  When the refrigerating machine oil O is in a low temperature state below the required temperature, the refrigerant is easily dissolved in the refrigerating machine oil O, and there is a concern that the viscosity of the refrigerating machine oil O will decrease or the amount of discharged oil will increase.

  Therefore, in the present embodiment, by controlling the opening / closing of the on-off valve 21, in a state where the refrigerating machine oil O is lower than the required temperature, the transport of the refrigerating machine oil O to the cooler 17 is stopped to stop the cooling, and the refrigerating machine oil is stopped. Cooling is possible only when O is higher than the required temperature.

  Thereby, the refrigerating machine oil O can be controlled to an appropriate temperature. Since the refrigerator oil O temperature and the refrigerant discharge gas temperature are in a proportional relationship, the opening / closing or opening degree of the on-off valve 21 may be controlled based on the refrigerant discharge gas temperature.

(Sixth embodiment)
FIG. 7 is a schematic plan view of the outdoor unit 31 of the air conditioner according to the sixth embodiment. The sixth embodiment is characterized in that the cooler 17 is forcibly cooled by an outdoor fan 32 of an outdoor unit 31 such as an air conditioner.

  That is, the outdoor unit 31 of the air conditioner according to the sixth embodiment includes the rotary compressor 1, the accumulator 14, the outlet pipe 16 and the return pipe 18 connected to the rotary compressor 1 in the outdoor unit unit case 33. The cooler 17, the outdoor heat exchanger 33, and the outdoor fan 32 connected through the outlet pipe 16 and the return pipe 18 are accommodated.

  The cooler 17 is also forcedly cooled by the outdoor fan 32 that cools the outdoor heat exchanger 33.

  As a cooling method of the cooler 17, there is a method of cooling using a separately installed radiator or fan unit. However, this method has a problem that the cost increases and the power consumption of the entire system increases.

  On the other hand, according to this embodiment, since the cooler 17 is also cooled by the outdoor fan 32 that cools the outdoor heat exchanger 33, both cost and power consumption can be reduced.

  And when using this outdoor unit 31 for an air conditioner, since the outdoor heat exchanger 33 acts as an evaporator at the time of heating, a low temperature blowing wind generate | occur | produces. Since this cold air is blown to the cooler 17 by the outdoor fan 32, the cooling effect of the cooler 17 is great. In addition, since the outdoor heat exchanger 33 acts as a condenser during cooling, the blown air is not low temperature, but the temperature of the refrigerating machine oil O is higher than the blown air. It can have the effect of being cooled.

  As mentioned above, although several embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of this invention. These novel embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the scope of the present invention. These embodiments and modifications thereof are included in the scope and gist of the present invention, and are included in the invention described in the claims and the equivalents thereof.

  DESCRIPTION OF SYMBOLS 1 ... Rotary compressor, 2 ... Sealed container, 4 ... Electric motor, 7A ... 1st cylinder, 7B ... 2nd cylinder, 10a ... 1st eccentric roller, 10b ... 2nd eccentric roller, 11a ... 1st Vane groove, 11b ... second vane groove, 12a ... first vane, 12b ... second vane, 13a ... first vane back chamber, 13b ... second vane back chamber, 13c ... lower opening, 13d DESCRIPTION OF SYMBOLS ... Upper opening part, 15 ... Lid for connection, 16 ... Outlet pipe, 17 ... Cooler, 18 ... Return pipe, O ... Refrigerating machine oil, Sa ... 1st cylinder chamber, Sb ... 2nd cylinder chamber.

Claims (4)

A sealed container;
Electric motors housed in the sealed containers, a compression mechanism driven by the electric motors, and refrigerating machine oil,
Comprising
In the cylinder forming the cylinder chamber in which the compression mechanism portion is driven by the electric motor to accommodate the eccentrically moving roller, the vane groove for accommodating the vane reciprocating while being in sliding contact with the outer peripheral surface of the roller, and the vane groove In a rotary compressor having a vane back chamber that includes a spring member that communicates and elastically presses the vane to the roller side at all times and has openings in the refrigerating machine oil formed at the upper and lower ends,
The lower end opening of the vane back chamber is closed by a lid member having an opening, and after the refrigerating machine oil discharged from the opening of the lid member is led out of the sealed container, the cooling is returned to the sealed container. A rotary compressor comprising a circuit and using a pump action generated by a reciprocating motion of the vane as power for circulating the refrigerating machine oil in the cooling circuit. 2. The rotary compressor according to claim 1, wherein the cooling circuit includes a cooler including a finned tube heat exchanger outside the sealed container. The said cooling circuit is provided with the opening-and-closing valve controlled to open and close according to the temperature of the discharge gas discharged outside from the refrigerating machine oil or the said airtight container in the middle of the circuit. Rotary compressor. The rotary compressor according to claim 2, an outdoor heat exchanger, an outdoor fan that blows air to the outdoor heat exchanger and air-cools the cooler,
An outdoor unit case that houses the outdoor fan, the rotary compressor, and the outdoor heat exchanger;
The outdoor unit of the air conditioner characterized by comprising.

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