JP6324624B2 - Refrigerant compressor and vapor compression refrigeration cycle apparatus equipped with the same - Google Patents

Description

  The present invention relates to a refrigerant compressor for compressing a refrigerant and a vapor compression refrigeration cycle apparatus including the refrigerant compressor.

  Conventionally, in heat pump equipment such as an air conditioner or a water heater, a vapor compression refrigeration cycle apparatus using a refrigerant compressor is generally used. In other words, heat pump equipment is equipped with a refrigeration cycle formed by connecting refrigerant compressors, radiators, expansion mechanisms, and evaporators with pipes, and performs operations according to applications (for example, air conditioning applications and hot water supply applications). It can be done.

  By the way, in recent years, energy-saving regulations for air-conditioning equipment have been strengthened in each country and are being changed to operating standards close to actual loads. In Japan, it was changed from A 2011 to APF (Annual Energy Consumption Efficiency) display, compared to the previous display of efficiency improvement with the average COP. In addition, the energy-saving standards for air conditioners and water heaters are expected to be changed to new standards that are closer to actual loads. For example, assuming that the rated heating capacity required at the start-up of the air conditioner is 100%, the heating capacity that is always required is about 10% to 50%, and the efficiency in this low load region has an effect on the APF rather than the rated capacity. Is big.

  For this reason, ON-OFF control has been used for a long time as a means for adjusting the cooling and heating capacity. However, this ON-OFF control has a problem that the temperature control fluctuation range and vibration noise increase, and a problem that energy saving is impaired. Therefore, in recent years, inverter control that makes the rotation speed of the electric motor that drives the refrigerant compressor variable has become widespread for the purpose of improving energy saving.

  Here, in recent years, since the air conditioner has been required to shorten the startup time and operate in a harsher environment (low temperature or high temperature), a rated capacity exceeding a certain level is required. On the other hand, with the development of highly insulated houses, the capacity required at all times is decreasing, and the capacity range during operation is expanding. For this reason, the rotation speed variable range of the refrigerant compressor by the inverter is expanded, and the rotation speed range in which high efficiency of the refrigerant compressor is required tends to be expanded. For this reason, it is difficult for the conventional air conditioner to maintain the high efficiency of the refrigerant compressor while continuously operating the refrigerant compressor by reducing the rotational speed under the low load capacity condition.

  Then, the refrigerant compressor using the means (mechanical capacity control means) that can change the excluded volume mechanically is attracting attention again. For example, Patent Documents 1 and 2 have two compression mechanism parts, a first compression mechanism part and a second compression mechanism part, and both compression mechanism parts are compression-operated at high load, and one of them at low load. A refrigerant compressor is disclosed in which the capacity is halved by operating the compression mechanism section in compression and the other compression mechanism section in idle cylinder operation (non-compression operation) to reduce the refrigerant circulation flow rate by half.

  In the refrigerant compressor described in Patent Document 1, the vane of the compression mechanism portion is reciprocally accommodated in the vane groove, and the rear end portion of the vane is located in the vane back chamber provided in communication with the vane groove. . The vane back chamber is configured to communicate with the internal space of the sealed container and receive pressure (high pressure) in the internal space, and high pressure acts on the rear end portion of the vane.

  In the compression operation state, a low-pressure refrigerant is guided to the cylinder chamber of the compression mechanism section to apply a low pressure or intermediate pressure to the vane tip, and a high pressure is applied to the rear end portion of the vane as described above. Thereby, a pressure difference arises between the vane front end and the rear end. In the compression operation state, due to the effect of the pressure difference, the tip of the vane is pressed so as to contact the piston, and a normal compression operation is performed.

  In the idle cylinder operation state, high pressure is applied to each of the front end portion and the rear end portion of the vane by guiding the high-pressure refrigerant to the cylinder chamber by the switching mechanism, and the pressure difference between the front end and the rear end of the vane is eliminated. By eliminating the pressure difference, the tip of the vane is separated from the outer peripheral surface of the piston. As a result, the compression action is not performed in the idle cylinder operation state.

  In the refrigerant compressor described in Patent Document 2, as in Patent Document 1, suction pressure (low pressure) is applied to the front end of the vane and discharge pressure (high pressure) is applied to the rear end during the compression operation. And in patent document 2, the permanent magnet which generate | occur | produces the attracting magnetic force which draws in the direction which spaces apart a vane from a piston is provided in the vane back chamber. Therefore, in Patent Document 2, a pressing force in a direction in which the vane is brought into contact with the piston acts on the vane, and at the same time, an attractive magnetic force in a direction in which the vane is separated from the piston acts. When the pressing force is smaller than the attractive magnetic force, the vane moves away from the piston and the cylinder resting operation is performed. When the pressing force is larger than the attractive magnetic force, the vane contacts the piston and the compression operation is performed.

  Since the refrigerant compressors described in Patent Documents 1 and 2 can reduce the refrigerant circulation flow rate by half by setting one of the compression mechanisms to a non-cylinder operation (non-compression operation). You can drive without dropping. Therefore, the compressor efficiency of the refrigerant compressor can be improved.

JP 2005-171847 A International Publication No. 2014/175429

  In the refrigerant compressor described in Patent Document 1, mechanical capacity control means based on the idle cylinder operation method is used in order to improve efficiency reduction under low load conditions. In this refrigerant compressor, as a mechanical capacity control means, a permanent magnet for adsorbing and holding the vane during the idle cylinder operation is provided in the vane back chamber. Further, the vane back chamber communicates with an oil reservoir in the sealed container in order to apply a high pressure to the rear end portion of the vane. Therefore, the metal pieces generated in each sliding portion in the sealed container and mixed in the lubricating oil are attracted to the permanent magnet provided in the vane back chamber and are easily collected around the vane. Therefore, this refrigerant compressor has a problem that the reliability of sliding parts such as vanes is lowered.

  Moreover, in the refrigerant compressor of patent document 2, it is necessary to control the attractive magnetic force from the permanent magnet which acts on a vane. However, if metal pieces in the lubricating oil adhere to the surface of the permanent magnet or yoke, the attractive magnetic force acting on the vane will vary, making it difficult to stably switch between compression operation and cylinder resting operation. There was a problem.

  The present invention has been made to solve the above-described problems, and can improve the reliability of the sliding portion, and can stably switch between a compression operation and a cylinder resting operation, and a refrigerant compressor, An object of the present invention is to provide a vapor compression refrigeration cycle apparatus including the same.

  A refrigerant compressor according to the present invention includes a sealed container storing lubricating oil, and a plurality of compression mechanisms accommodated in the sealed container, and each of the plurality of compression mechanisms includes a cylinder having a cylinder chamber; A piston that rotates eccentrically in the cylinder chamber, a vane that has a tip portion that contacts the piston, and that divides the cylinder chamber into a plurality of spaces; and is formed in the cylinder and reciprocally accommodates the vane. A vane groove and a vane back chamber that is formed on an outer peripheral side of the vane groove of the cylinder and accommodates a rear end portion of the vane, and at least one of the plurality of compression mechanisms The compression mechanism includes a compression operation in which the refrigerant is compressed in a state where the tip of the vane is in contact with the piston, and the refrigerant is compressed by moving the tip of the vane away from the piston. A cylinder resting mechanism for switching between a cylinder resting operation, and the cylinder resting mechanism includes a magnetic body that generates an attractive magnetic force that attracts the vane in a direction away from the piston. A first surface facing the vane back chamber and facing a rear end portion of the vane, and the at least one compression mechanism includes lubricating oil stored in the sealed container, An oil supply passage for supplying the vane back chamber is formed along a second surface of the magnetic body, the direction of which is different from the first surface, and a part of the inner wall surface of the oil supply passage is , Constituted by the second surface.

  The vapor compression refrigeration cycle apparatus according to the present invention includes the refrigerant compressor according to the present invention, a radiator that dissipates heat from the refrigerant compressed by the refrigerant compressor, and an expansion mechanism that expands the refrigerant flowing out of the radiator. And an evaporator that absorbs heat by the refrigerant flowing out of the expansion mechanism.

  According to the present invention, it is possible to prevent the metal piece mixed in the lubricating oil from entering the vane back chamber, so that the reliability of the sliding portion can be improved, and the compression operation and the cylinder resting operation can be stably performed. Can be switched.

It is a schematic longitudinal cross-sectional view which shows the structure of the refrigerant compressor 100 which concerns on Embodiment 1 of this invention. It is a schematic cross-sectional view showing the configuration of the first compression mechanism 10 of the refrigerant compressor 100 according to Embodiment 1 of the present invention. It is a schematic cross-sectional view showing the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to Embodiment 1 of the present invention. It is a schematic longitudinal cross-sectional view which shows the structure of the 2nd compression mechanism 20 of the refrigerant compressor 100 which concerns on Embodiment 1 of this invention, and is a figure which expands and shows the IV section of FIG. 3 is a schematic side view showing a configuration of second compression mechanism 20 of refrigerant compressor 100 according to Embodiment 1 of the present invention as viewed along the extending direction of vane groove 29. FIG. It is a schematic longitudinal cross-sectional view which shows the modification of the structure of the 2nd compression mechanism 20 of the refrigerant compressor 100 which concerns on Embodiment 1 of this invention. It is a schematic longitudinal cross-sectional view which shows the structure of the 2nd compression mechanism 20 of the refrigerant compressor 100 which concerns on Embodiment 2 of this invention. It is a schematic top view which shows the structure of the 2nd compression mechanism 20 of the refrigerant compressor 100 which concerns on Embodiment 2 of this invention. 6 is a schematic side view showing a configuration of second compression mechanism 20 of refrigerant compressor 100 according to Embodiment 3 of the present invention as viewed along the extending direction of vane groove 29. FIG. It is a schematic cross-sectional view which shows the XX cross section of FIG. It is a schematic cross-sectional view which shows the structure of the 2nd compression mechanism 20 of the refrigerant compressor 100 which concerns on Embodiment 4 of this invention. It is a schematic longitudinal cross-sectional view which shows the structure of the 2nd compression mechanism 20 of the refrigerant compressor 100 which concerns on Embodiment 5 of this invention. It is a schematic longitudinal cross-sectional view which shows the structure of the refrigerant compressor 100 which concerns on Embodiment 6 of this invention. It is a refrigerant circuit diagram which shows the structure of the vapor compression refrigeration cycle apparatus 500 which concerns on Embodiment 7 of this invention.

  Hereinafter, an example of a refrigerant compressor and a vapor compression refrigeration cycle apparatus according to the present invention will be described based on the drawings. In the drawings shown below, the relationship between the sizes of the constituent members may be different from the actual ones. In addition, the three-dimensional positional relationship between the discharge port and the cylinder suction channel does not necessarily match in the longitudinal sectional view and the transverse sectional view.

Embodiment 1 FIG.
A refrigerant compressor according to Embodiment 1 of the present invention will be described. FIG. 1 is a schematic longitudinal sectional view showing a configuration of a refrigerant compressor 100 according to the present embodiment. FIG. 2 is a schematic cross-sectional view showing the configuration of the first compression mechanism 10 of the refrigerant compressor 100 according to the present embodiment. FIG. 3 is a schematic cross-sectional view showing the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment. In the present embodiment, as the refrigerant compressor 100, a vertical rotary compressor is illustrated. In the refrigerant compressor 100 shown in FIGS. 1 to 3, the first compression mechanism 10 is in a compression operation state in which the refrigerant is compressed, and the second compression mechanism 20 is not compressed in the refrigerant. It is in a non-compression operation state (cylinder operation state).

  The refrigerant compressor 100 is one of the components of a refrigeration cycle employed in a heat pump device such as an air conditioner or a water heater. The refrigerant compressor 100 has a function of sucking a gaseous fluid, compressing it, and discharging it in a high temperature / high pressure state.

  The refrigerant compressor 100 according to the present embodiment includes a compression mechanism 99 having a first compression mechanism 10 and a second compression mechanism 20 in the internal space 7 of the sealed container 3, and the first compression mechanism 10 and the second compression mechanism 20. And an electric motor 8 that drives the motor via a drive shaft 5.

  The airtight container 3 is, for example, a cylindrical airtight container in which the upper end and the lower end are closed. At the bottom of the hermetic container 3, there is provided a lubricating oil reservoir 3 a (oil reservoir) in which lubricating oil that lubricates the compression mechanism 99 is stored. In the state shown in FIG. 1, the oil level of the lubricating oil is located above both the first compression mechanism 10 and the second compression mechanism 20. A compressor discharge pipe 2 is provided on the upper part of the sealed container 3 so as to communicate with the internal space 7 of the sealed container 3.

  The electric motor 8 includes a stator 8b and a rotor 8a. The electric motor 8 is driven at a variable rotational speed by, for example, inverter control. The stator 8b is formed in a substantially cylindrical shape. The outer peripheral portion of the stator 8b is fixed to the inner peripheral portion of the sealed container 3 by, for example, shrink fitting. A coil to which electric power is supplied from an external power source is wound around the stator 8b. The rotor 8a is formed in a substantially cylindrical shape. The rotor 8a is disposed on the inner peripheral side of the stator 8b with a predetermined distance from the inner peripheral surface of the stator 8b. The drive shaft 5 is fixed to the rotor 8a. The electric motor 8 and the compression mechanism 99 are connected via the drive shaft 5. That is, as the electric motor 8 rotates, the rotational power is transmitted to the compression mechanism 99 via the drive shaft 5.

  The drive shaft 5 is formed between a long shaft portion 5a constituting the upper portion of the drive shaft 5, a short shaft portion 5b constituting the lower portion of the drive shaft, and the long shaft portion 5a and the short shaft portion 5b. Eccentric pin shaft portions 5c and 5d and an intermediate shaft portion 5e. Here, the eccentric pin shaft portion 5c has a central axis that is eccentric by a predetermined distance from the central axes of the long shaft portion 5a and the short shaft portion 5b, and is disposed in the first cylinder chamber 12 of the first compression mechanism 10 described later. Is done. Further, the eccentric pin shaft portion 5d has a central axis that is eccentric by a predetermined distance from the central axes of the long shaft portion 5a and the short shaft portion 5b, and is disposed in a second cylinder chamber 22 of the second compression mechanism 20 described later. The The eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are provided with phases shifted by 180 degrees from each other. The eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are connected by an intermediate shaft portion 5e. The intermediate shaft portion 5e is disposed in a through hole of the intermediate partition plate 4 described later. The long shaft portion 5 a of the drive shaft 5 is rotatably supported by the bearing portion 60 a of the first support member 60. The short shaft portion 5 b is rotatably supported by the bearing portion 70 a of the second support member 70. That is, when the drive shaft 5 rotates, the eccentric pin shaft portions 5c and 5d perform eccentric rotational movement in the first cylinder chamber 12 and the second cylinder chamber 22, respectively.

  The compression mechanism 99 includes a rotary first compression mechanism 10 provided in the upper part and a rotary second compression mechanism 20 provided in the lower part. The first compression mechanism 10 and the second compression mechanism 20 are disposed below the electric motor 8. The compression mechanism 99 includes a first support member 60, a first cylinder 11 that constitutes the first compression mechanism 10, an intermediate partition plate 4, and a second cylinder 21 that constitutes the second compression mechanism 20 from the upper side to the lower side. , And the second support member 70 is sequentially laminated.

  The first compression mechanism 10 includes a first cylinder 11, a first piston 13, a first vane 14, and the like. The first cylinder 11 is a flat plate member in which a substantially cylindrical through hole that is substantially concentric with the drive shaft 5 (more specifically, the long shaft portion 5a and the short shaft portion 5b) is formed in a vertical direction. One end portion (upper end portion in FIG. 1) of the through hole is closed by the flange portion 60b of the first support member 60, and the other end portion (lower end portion in FIG. 1) is formed by the intermediate partition plate 4. The first cylinder chamber 12 is formed by being closed.

  A first piston 13 is provided in the first cylinder chamber 12 of the first cylinder 11. The first piston 13 is formed in a ring shape, and is slidably provided on the eccentric pin shaft portion 5 c of the drive shaft 5. Further, a vane groove 19 that communicates with the first cylinder chamber 12 and extends in the radial direction of the first cylinder chamber 12 is formed in the first cylinder 11. A first vane 14 is slidably provided in the vane groove 19. The first cylinder chamber 12 is divided into a suction chamber 12a and a compression chamber 12b by the front end portion 14a of the first vane 14 coming into contact with the outer peripheral portion of the first piston 13.

  A vane back chamber 15 is formed in the first cylinder 11 on the outer peripheral side of the vane groove 19, that is, on the rear side of the first vane 14. The vane back chamber 15 is provided so as to penetrate the first cylinder 11 in the vertical direction. The upper opening of the vane back chamber 15 is partially open to the internal space 7 (the space outside the first cylinder 11) of the sealed container 3. As a result, the lubricating oil stored in the lubricating oil storage unit 3 a can flow into the vane back chamber 15. The lubricating oil that has flowed into the vane back chamber 15 flows between the vane groove 19 and the first vane 14 and reduces the sliding resistance between the two. As will be described later, the refrigerant compressor 100 according to the present embodiment is configured such that the refrigerant compressed by the compression mechanism 99 is discharged into the internal space 7 of the sealed container 3. For this reason, the vane back chamber 15 has the same high-pressure atmosphere as the internal space 7 of the sealed container 3.

  The second compression mechanism 20 includes a second cylinder 21, a second piston 23, a second vane 24, and the like. The second cylinder 21 is a flat plate member in which a substantially cylindrical through hole that is substantially concentric with the drive shaft 5 (more specifically, the long shaft portion 5a and the short shaft portion 5b) is vertically formed. One end portion (upper end portion in FIG. 1) of the through hole is closed by the intermediate partition plate 4, and the other end portion (lower end portion in FIG. 1) is formed by the flange portion 70 b of the second support member 70. The second cylinder chamber 22 is formed by being closed.

  A second piston 23 is provided in the second cylinder chamber 22 of the second cylinder 21. The second piston 23 is formed in a ring shape and is slidably provided on the eccentric pin shaft portion 5 d of the drive shaft 5. The second cylinder 21 has a vane groove 29 that communicates with the second cylinder chamber 22 and extends in the radial direction of the second cylinder chamber 22. A second vane 24 is slidably provided in the vane groove 29. The second cylinder chamber 22 is divided into a suction chamber and a compression chamber in the same manner as the first cylinder chamber 12 by the tip 24 a of the second vane 24 coming into contact with the outer peripheral portion of the second piston 23.

  A vane back chamber 25 is formed in the second cylinder 21 on the outer peripheral side of the vane groove 29, that is, on the rear side of the second vane 24. The vane back chamber 25 is provided so as to penetrate the second cylinder 21 in the vertical direction. The upper and lower openings of the vane back chamber 25 are closed by the intermediate partition plate 4 and the flange portion 70 b of the second support member 70. The vane back chamber 25 communicates with the internal space 7 (the space outside the second cylinder 21) of the sealed container 3 via oil supply passages 55a and 55b described later. For this reason, the vane back chamber 25 has the same high-pressure atmosphere as the internal space 7 of the sealed container 3. The lubricating oil stored in the lubricating oil storage unit 3a can flow into the vane back chamber 25 from the outer peripheral side of the second cylinder 21 via the oil supply passages 55a and 55b. The lubricating oil that has flowed into the vane back chamber 25 flows between the vane groove 29 and the second vane 24 and reduces the sliding resistance between the two.

  The first cylinder 11 and the second cylinder 21 are connected to a suction muffler 6 for allowing a gaseous refrigerant to flow into the first cylinder chamber 12 and the second cylinder chamber 22. Specifically, the suction muffler 6 includes a container 6b, an inflow pipe 6a that guides the low-pressure refrigerant from the evaporator to the container 6b, and a gaseous refrigerant out of the refrigerant stored in the container 6b in the first cylinder chamber of the first cylinder 11. 12, and an outflow pipe 6 d for guiding a gaseous refrigerant out of the refrigerant stored in the container 6 b to the second cylinder chamber 22 of the second cylinder 21. The outflow pipe 6 c of the suction muffler 6 is connected to a cylinder suction passage 17 that communicates with the first cylinder chamber 12 of the first cylinder 11. The outflow pipe 6 d of the suction muffler 6 is connected to a cylinder suction passage 27 that communicates with the second cylinder chamber 22 of the second cylinder 21.

  Further, the first cylinder 11 is formed with a discharge port 18 for discharging a gaseous refrigerant compressed in the first cylinder chamber 12. The discharge port 18 communicates with a through hole (not shown) formed in the flange portion 60 b of the first support member 60. The through hole is provided with an on-off valve (not shown) that opens when the inside of the first cylinder chamber 12 becomes a predetermined pressure or higher. In addition, a discharge muffler 63 is attached to the first support member 60 so as to cover the on-off valve (that is, the through hole of the flange portion 60b). Similarly, the second cylinder 21 is formed with a discharge port 28 for discharging the gaseous refrigerant compressed in the second cylinder chamber 22. The discharge port 28 communicates with a through hole (not shown) formed in the flange portion 70 b of the second support member 70. The through-hole is provided with an on-off valve (not shown) that opens when the inside of the second cylinder chamber 22 becomes a predetermined pressure or higher. Further, a discharge muffler 73 is attached to the second support member 70 so as to cover the on-off valve (that is, the through hole of the flange portion 70b).

  As described above, the first compression mechanism 10 and the second compression mechanism 20 have the same configuration in the basic configuration. However, the first compression mechanism 10 and the second compression mechanism 20 have different configurations as described below in a detailed configuration. In the following description, out of the forces acting on the first vane 14 and the second vane 24, the force in the direction of contacting the first piston 13 and the second piston 23 is defined as the first force. Of the forces acting on the second vane 24, the force in the direction away from the second piston 23 is defined as the second force.

  The first cylinder chamber 12 and the second cylinder chamber 22 are always in communication with the suction pressure space, and the vane back chambers 15 and 25 are always in communication with the discharge pressure space. Therefore, suction pressure acts on the front end portions 14a and 24a of the first vane 14 and the second vane 24, and discharge pressure acts on the rear end portions 14b and 24b of the first vane 14 and the second vane 24, respectively. Act. A first force acts on the first vane 14 and the second vane 24 due to a difference in pressure acting on the front end portions 14a and 24a and the rear end portions 14b and 24b.

  The vane back chamber 15 of the first compression mechanism 10 is provided with a compression spring 40 that urges the first vane 14 in a direction to contact the first piston 13. That is, the first force acts on the first vane 14 of the first compression mechanism 10 even when there is no difference in the pressure acting on the front end portion 14a and the rear end portion 14b.

  The second compression mechanism 20 includes a cylinder resting mechanism 50 that switches between a compression operation and a cylinder resting operation. The cylinder resting mechanism 50 includes a magnetic body 53 that generates an attractive magnetic force that attracts the second vane 24 in a direction away from the second piston 23. The magnetic body 53 of this example includes a permanent magnet 51 and a yoke 52. The permanent magnet 51 is disposed behind the second vane 24. The yoke 52 is laminated on the surface of the permanent magnet 51 on the second vane 24 side. The permanent magnet 51 and the yoke 52 are fixed to the second cylinder 21 by, for example, its own magnetic force. The permanent magnet 51 and the yoke 52 may be held by flow path forming members 54a and 54b described later. The surface 53 a of the magnetic body 53 (that is, the surface of the yoke 52) faces the rear end portion 24 b of the second vane 24. The surface 53 a of the magnetic body 53 is provided facing the vane back chamber 25 and constitutes a part of the inner wall surface of the vane back chamber 25.

  The attractive force of the permanent magnet 51 acts on the second vane 24 as the second force in the direction away from the second piston 23. The attractive magnetic force (second force) acting on the second vane 24 has a characteristic of increasing as the second vane 24 approaches the permanent magnet 51. In addition, although the magnetic body 53 of this example is comprised with the permanent magnet 51 and the yoke 52, you may be comprised only with the permanent magnet 51. FIG.

  A first force and a second force always act on the second vane 24. For this reason, in the second compression mechanism 20, the compression operation state and the cylinder deactivation operation state autonomously switch depending on the magnitude relationship between the first force and the second force acting on the second vane 24. That is, when the first force is greater than the second force, the tip 24a of the second vane 24 comes into contact with the second piston 23, so that the second compression mechanism 20 enters a compression operation state. When the second force is greater than the first force, the second vane 24 is separated from the second piston 23 and is attracted to the surface 53a of the magnetic body 53, and no compression chamber is formed in the second cylinder chamber 22, The second compression mechanism 20 enters a cylinder resting operation state. Once the second vane 24 is separated from the second piston 23, the second vane 24 approaches the permanent magnet 51, so that the second force acting on the second vane 24 increases.

  In order to switch from the idle cylinder operation state to the compression operation state, the first force needs to be greater than the second force. However, the second force when the second vane 24 is attracted to the surface 53 a of the magnetic body 53 is larger than the second force when the second vane 24 is separated from the second piston 23. For this reason, the 1st force required in order to switch from a cylinder rest operation state to a compression operation state turns into a force larger than the 1st force when it switches from a compression operation state to a cylinder rest operation state.

  Next, the operation | movement at the time of compressing a refrigerant | coolant with both the 1st compression mechanism 10 and the 2nd compression mechanism 20 is demonstrated. This operation is the same as that of a normal rotary compressor in which the compression mechanism does not enter the cylinder resting state. Specifically, the operation is as follows.

  When electric power is supplied to the electric motor 8, the drive shaft 5 is rotated counterclockwise (in the direction of the thick arrow in FIGS. 2 and 3) when viewed from above by the electric motor 8. By rotating the drive shaft 5, the eccentric pin shaft portion 5 c moves eccentrically in the first cylinder chamber 12, and the eccentric pin shaft portion 5 d moves eccentrically in the second cylinder chamber 22. The eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are eccentrically rotated so that the phases are shifted by 180 degrees.

  Along with the eccentric rotational movement of the eccentric pin shaft portion 5 c, the first piston 13 rotates eccentrically in the first cylinder chamber 12, and the first cylinder chamber passes through the outlet pipe 6 c of the suction muffler 6 via the cylinder suction passage 17. The low-pressure gaseous refrigerant sucked into 12 is compressed. Similarly, along with the eccentric rotational movement of the eccentric pin shaft portion 5d, the second piston 23 rotates eccentrically in the second cylinder chamber 22, and the second piston 23 passes through the outlet pipe 6d of the suction muffler 6 via the cylinder suction flow path 27. The low-pressure gaseous refrigerant sucked into the two-cylinder chamber 22 is compressed.

  The gaseous refrigerant compressed in the first cylinder chamber 12 is discharged into the discharge muffler 63 from the discharge port 18 at a predetermined pressure, and then discharged from the discharge port of the discharge muffler 63 into the internal space 7 of the sealed container 3. Is done. Further, the gaseous refrigerant compressed in the second cylinder chamber 22 is discharged into the discharge muffler 73 from the discharge port 28 when a predetermined pressure is reached, and then the internal space 7 of the sealed container 3 from the discharge port of the discharge muffler 73. Discharged. Then, the high-pressure gaseous refrigerant discharged into the internal space 7 of the sealed container 3 is discharged from the compressor discharge pipe 2 to the outside of the sealed container 3.

  When the refrigerant is compressed by the first compression mechanism 10 and the second compression mechanism 20, the refrigerant compression operation is repeated in each of the first compression mechanism 10 and the second compression mechanism 20.

  Next, the operation when the second compression mechanism 20 is in the idle cylinder operation state will be described. Even during the operation, the first vane 14 of the first compression mechanism 10 is pressed by the compression spring 40 and is always in contact with the first piston 13. Thereby, in the 1st compression mechanism 10, the refrigerant | coolant compression operation similar to the above is performed. Therefore, only the operation of the second compression mechanism 20 will be described below.

  When the second compression mechanism 20 is in the compression operation state, the discharge pressure acts on the rear end portion 24b of the second vane 24 via the lubricating oil. At this time, the pressing force (first force) acting on the second vane 24 due to the pressure difference between the front end portion 24 a and the rear end portion 24 b of the second vane 24 exceeds the attractive magnetic force (second force) of the permanent magnet 51. Yes. As a result, the tip 24 a of the second vane 24 is pressed against the outer peripheral surface of the second piston 23. Therefore, in the second compression mechanism 20, the refrigerant is compressed as the drive shaft 5 rotates.

  On the other hand, immediately after the start of operation of the refrigerant compressor 100 or in a state where the load of the refrigerant compressor 100 is low, the pressure in the internal space 7 of the sealed container 3 is relatively low. For this reason, the attractive magnetic force (second force) of the permanent magnet 51 exceeds the pressing force (first force) generated by the pressure difference acting on the front end portion 24a and the rear end portion 24b of the second vane 24. Thereby, the 2nd vane 24 spaces apart from the outer peripheral surface of the 2nd piston 23, and the 2nd compression mechanism 20 will be in a cylinder resting operation state.

  And the attraction | suction magnetic force with respect to the 2nd vane 24 increases because the front-end | tip part 24a of the 2nd vane 24 spaces apart from the outer peripheral surface of the 2nd piston 23, and the rear-end part 24b of the 2nd vane 24 approaches the permanent magnet 51. . As a result, the second vane 24 further moves away from the second piston 23, and the rear end 24b of the second vane 24 comes into contact with the yoke 52 and is held by suction.

  Next, the operation of releasing the cylinder resting operation state of the second compression mechanism 20 will be described. When the pressure (that is, the discharge pressure) in the inner space 7 of the sealed container 3 is increased in the closed cylinder operation state, the pressure acts on the second vane 24 due to the pressure difference between the front end portion 24a and the rear end portion 24b of the second vane 24. The pressing force (first force) exceeds the attractive magnetic force (second force) by the permanent magnet 51. If it will be in this state, the 2nd vane 24 will leave | separate from the yoke 52, and the adsorption | suction holding | maintenance of the 2nd vane 24 will be cancelled | released.

  And when the rear-end part 24b of the 2nd vane 24 leaves | separates from the permanent magnet 51, the attraction magnetic force with respect to the 2nd vane 24 reduces, and the difference of 1st force and 2nd force becomes large. As a result, the second vane 24 further moves to the second piston 23 side, the tip 24a of the second vane 24 is pressed against the outer peripheral surface of the second piston 23, and the second compression mechanism 20 starts the refrigerant compression operation. To do.

  As described above, the permanent magnet 51 and the yoke 52 are provided in the vane back chamber 25 in order to switch the operation state of the second compression mechanism 20. However, when the refrigerant compressor 100 is driven, a metal piece having a size of several μm to several hundred μm is generated by sliding of the vane, the piston, the drive shaft, and the like in the compression mechanism 99. The generated metal piece flows into the internal space 7 of the sealed container 3 together with the compressed refrigerant and lubricating oil. The metal piece in the internal space 7 flows into the vane back chamber 25 together with the lubricating oil and is likely to be adsorbed to the magnetic body 53 by the attractive magnetic force. For example, if a metal piece adheres to the surface 53 a of the magnetic body 53, the attractive magnetic force acting on the second vane 24 varies. For this reason, the pressure condition under which the operation state of the second compression mechanism 20 is switched may change, and it may be difficult to stably control the operation state of the second compression mechanism 20. In the present embodiment, this problem is solved by configuring as follows.

  FIG. 4 is a schematic longitudinal sectional view showing the configuration of the second compression mechanism 20, and is an enlarged view of the IV portion (portion surrounded by a broken line) in FIG. FIG. 5 is a schematic side view showing a configuration in which the second compression mechanism 20 is viewed along the extending direction of the vane groove 29. As shown in FIGS. 4 and 5, flow path forming members 54 a and 54 b are provided at the upper and lower ends in the axial direction of the vane back chamber 25 of the second cylinder 21. The flow path forming members 54a and 54b form oil supply flow paths 55a and 55b that connect the internal space 7 and the vane back chamber 25, respectively. The flow path forming member 54a and the flow path forming member 54b, that is, the oil supply flow path 55a and the oil supply flow path 55b are formed substantially symmetrically in the vertical direction. The lubricating oil in the lubricating oil storage unit 3a is supplied from the outer peripheral side of the second cylinder 21 to the vane back chamber 25 through the oil supply passages 55a and 55b. The lubricating oil supplied to the vane back chamber 25 flows into a sliding portion between the second vane 24 and the vane groove 29. In FIG. 4, an example of the flow of the lubricating oil is indicated by arrows.

  The flow path forming members 54a and 54b are formed using a nonmagnetic material. The flow path forming members 54a and 54b are attached so as to sandwich the second cylinder 21 from above and below in the axial direction. The flow path forming members 54 a and 54 b may be fixed to the upper surface and the lower surface of the second cylinder 21, respectively, or may be fixed to the outer peripheral surface of the intermediate partition plate 4 and the outer peripheral surface of the second support member 70. .

  The oil supply passage 55 a extends in parallel to the upper side surface 53 b of the magnetic body 53 and extends in the direction along the radial direction of the second cylinder 21. The inlet 55a1 of the oil supply passage 55a is provided at the rear end portion (outer end portion) of the flow passage forming member 54a and faces the inner peripheral surface of the sealed container 3. A part of the inner wall surface that defines the oil supply passage 55 a is configured by the upper side surface 53 b of the magnetic body 53. Similarly, the oil supply channel 55 b extends in parallel to the lower surface 53 c of the magnetic body 53 and in a direction along the radial direction of the second cylinder 21. The inlet 55b1 of the oil supply passage 55b is provided at the rear end (outer end) of the flow passage forming member 54b and faces the inner peripheral surface of the sealed container 3. A part of the inner wall surface that defines the oil supply channel 55 b is configured by a lower side surface 53 c of the magnetic body 53. The upper side surface 53b and the lower side surface 53c of the magnetic body 53 are surfaces having different directions from the surface 53a of the magnetic body 53. In the flow of lubricating oil in the oil supply passage 55a, the surface 53a is disposed on the downstream side of the upper side surface 53b. Further, in the flow of the lubricating oil in the oil supply passage 55b, the surface 53a is disposed on the downstream side of the lower side surface 53c.

  The width W1 of the oil supply passage 55a in the direction along the upper side surface 53b is limited to be equal to or smaller than the width W3 of the magnetic body 53 (W1 ≦ W3). The height H1 of the oil supply passage 55a in the direction orthogonal to the upper side surface 53b is included in the range of the magnetic field having a predetermined strength generated from the permanent magnet 51 in the side view as shown in FIG. For example, it is set to 10 mm or less. Thereby, when the metal pieces 80 are mixed in the lubricating oil flowing through the oil supply passage 55 a, all the metal pieces 80 pass through the range of the magnetic field generated from the permanent magnet 51. Therefore, the metal piece 80 in the lubricating oil is captured by the magnetic force of the permanent magnet 51 before entering the vane back chamber 25 and is attracted to the upper side surface 53 b of the magnetic body 53. Therefore, it is possible to prevent the metal piece 80 from entering the vane back chamber 25 or the sliding portion through the oil supply passage 55a. Further, since the metal piece 80 in the lubricating oil can be prevented from entering the vane back chamber 25, the metal piece 80 can also be prevented from being adsorbed to the surface 53a of the magnetic body 53.

  For the same reason, the width W2 of the oil supply passage 55b in the direction along the lower side surface 53c is limited to be equal to or smaller than the width W3 of the magnetic body 53 (W2 ≦ W3). The height H2 of the oil supply passage 55b in the direction orthogonal to the lower side surface 53c is set to 10 mm or less, for example. Thereby, it can prevent that the metal piece 80 penetrate | invades into the vane back chamber 25 or a sliding part through the oil supply flow path 55b, and also prevents that the metal piece 80 is adsorb | sucked to the surface 53a of the magnetic body 53. Can do.

  Further, mesh members 56a and 56b made of a metal material such as an iron-based material are provided on the downstream side of the upper side surface 53b in the oil supply passage 55a and on the downstream side of the lower side surface 53c in the oil supply passage 55b, respectively. ing. The mesh members 56 a and 56 b of this example are disposed in the vicinity of the boundary between the oil supply passages 55 a and 55 b and the vane back chamber 25. The mesh members 56 a and 56 b are members that allow passage of the lubricating oil and prevent passage of the metal piece 80. The mesh members 56a and 56b in this example are fixed by being sandwiched between the second cylinder 21, the intermediate partition plate 4, and the second support member 70, respectively. By providing the mesh members 56a and 56b, the small metal piece 80 that cannot be captured by the magnetic force of the permanent magnet 51 can be captured by the mesh members 56a and 56b.

  The mesh members 56 a and 56 b may be disposed in contact with the magnetic body 53. In this case, since the mesh members 56a and 56b can be magnetized and the metal piece 80 can be adsorbed by the mesh members 56a and 56b, the effect of capturing the metal piece 80 can be further enhanced. When the mesh members 56a and 56b are positively magnetized, for example, S45C, S25C, or the like is used as a material for forming the mesh members 56a and 56b.

  FIG. 6 is a schematic longitudinal sectional view showing a modification of the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment. In this modification, the mesh members 56a and 56b are inserted into the oil supply passages 55a and 55b in a rolled state, respectively. Thereby, mesh member 56a, 56b is fixed to the predetermined position in oil supply flow path 55a, 55b by the restoring force which is going to return to an original shape.

  As described above, in this embodiment, part of the inner wall surfaces of the oil supply passages 55a and 55b are the upper side surface 53b and the lower side surface 53c, which are different from the surface 53a in the magnetic body 53 that attracts the second vane 24. It is comprised by. Thereby, the metal piece 80 mixed in the lubricating oil flowing through the oil supply passages 55a and 55b can be captured by the upper side surface 53b and the lower side surface 53c by the magnetic force of the magnetic body 53 before flowing into the vane back chamber 25. . For this reason, although the configuration is simple, the metal piece 80 can be prevented from entering the sliding portion, and the reliability of the sliding portion can be improved. In the present embodiment, since the metal piece 80 can be captured before the metal piece 80 reaches the surface 53a of the magnetic body 53, it is possible to prevent variation in the attractive magnetic force acting on the second vane 24. Thus, it is possible to stably switch between the compression operation and the idle cylinder operation. Moreover, in this Embodiment, since the oil supply flow paths 55a and 55b are narrowed to the size in which the magnetic force of the magnetic body 53 acts effectively, the capture effect of the metal piece 80 can be further enhanced.

  In the present embodiment, the mesh members 56a and 56b are arranged on the downstream side of the upper side surface 53b and the lower side surface 53c of the magnetic body 53 in the flow of the lubricating oil in the oil supply passages 55a and 55b. For this reason, in the mesh members 56a and 56b, only the metal piece 80 that could not be removed by the upper side surface 53b and the lower side surface 53c is removed. Therefore, clogging of the mesh members 56a and 56b can be suppressed, and the life of the mesh members 56a and 56b can be extended.

  Further, in the present embodiment, the vane back chamber 25 and the lubricating oil storage unit 3a are always in communication via the oil supply passages 55a and 55b, so that a sufficient amount of oil supply is ensured with respect to the vane back chamber 25. be able to.

Embodiment 2. FIG.
A refrigerant compressor according to Embodiment 2 of the present invention will be described. In the first embodiment, the oil supply channels 55a and 55b are configured to extend in parallel along the upper side surface 53b and the lower side surface 53c of the magnetic body 53, respectively. If the oil supply passages 55a and 55b are configured as follows, the metal piece 80 can be more reliably prevented from entering the vane back chamber 25. Note that components that are not particularly described in this embodiment mode are the same as those in Embodiment Mode 1, and the same functions and configurations are described using the same reference numerals.

  FIG. 7 is a schematic longitudinal sectional view showing the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment. FIG. 8 is a schematic top view showing the configuration of the second compression mechanism 20. As shown in FIGS. 7 and 8, in the present embodiment, in comparison with the first embodiment, the inlet 55a1 of the oil supply passage 55a is formed on the upper surface of the flow passage forming member 54a, and the oil supply passage 55b. Is different at least in that the inflow port 55b1 is formed on the lower surface of the flow path forming member 54b.

  In the present embodiment, a part of the oil supply channel 55 a on the inlet 55 a 1 side extends perpendicularly to the upper side surface 53 b of the magnetic body 53. The oil supply passage 55a is bent substantially at a right angle while striking the upper side surface 53b. That is, a part of the inner wall surface located outside in the bent portion of the oil supply passage 55 a is configured by the upper side surface 53 b of the magnetic body 53. Similarly, a part of the oil supply passage 55b on the inlet 55b1 side extends orthogonally to the lower surface 53c of the magnetic body 53. Further, the oil supply passage 55b is bent substantially at a right angle against the lower side surface 53c. That is, a part of the inner wall surface located outside in the bent portion of the oil supply passage 55 b is configured by the lower side surface 53 c of the magnetic body 53.

  The lubricating oil flowing into the oil supply passage 55a from the inflow port 55a1 first flows toward the upper side surface 53b of the magnetic body 53, and collides with the upper side surface 53b of the magnetic body 53 due to inertia at the bent portion of the oil supply passage 55a. , Flows into the vane back chamber 25. Similarly, the lubricating oil flowing into the oil supply passage 55b from the inflow port 55b1 first flows toward the lower surface 53c of the magnetic body 53, and collides with the lower surface 53c of the magnetic body 53 due to inertia at the bent portion of the oil supply passage 55b. Then, it flows into the vane back chamber 25.

  Thereby, the metal piece 80 mixed in the lubricating oil passes through the vicinity of the upper side surface 53b or the lower side surface 53c where the magnetic field generated by the permanent magnet 51 is strong before flowing into the vane back chamber 25. For this reason, the metal piece 80 in the lubricating oil can be more reliably adsorbed to the upper side surface 53b or the lower side surface 53c. Therefore, in the present embodiment, it is possible to obtain a higher metal strip 80 removal effect than in the first embodiment.

Embodiment 3 FIG.
A refrigerant compressor according to Embodiment 3 of the present invention will be described. In the first embodiment, the oil supply channels 55a and 55b are configured to extend in parallel along the upper side surface 53b and the lower side surface 53c of the magnetic body 53, respectively. Even if the oil supply passage is configured as described below, the metal piece 80 can be prevented from entering the vane back chamber 25. Note that components that are not particularly described in this embodiment mode are the same as those in Embodiment Mode 1, and the same functions and configurations are described using the same reference numerals.

  FIG. 9 is a schematic side view showing the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment as viewed along the extending direction of the vane groove 29. FIG. 10 is a schematic cross-sectional view showing the XX cross section of FIG. As shown in FIGS. 9 and 10, in the present embodiment, at least a part of the oil supply passages 55 c and 55 d is formed in the second cylinder 21.

  The oil supply passage 55 c extends in a direction substantially parallel to the radial direction of the second cylinder 21 in parallel with the left side surface 53 d (the right side surface in FIG. 10) of the magnetic body 53. The oil supply passage 55d extends in a direction substantially parallel to the radial direction of the second cylinder 21 in parallel with the right side surface 53e (the left side surface in FIG. 10) of the magnetic body 53. Each of the oil supply channels 55 c and 55 d has a bottomed groove shape formed from the upper surface side of the second cylinder 21. The inlet 55c1 of the oil supply passage 55c is provided upward at the end of the oil supply passage 55c located at the outer peripheral portion of the second cylinder 21. The inlet 55d1 of the oil supply passage 55d is provided upward at the end of the oil supply passage 55d located on the outer peripheral portion of the second cylinder 21. A portion other than the inlet 55c1 in the upper portion of the oil supply passage 55c and a portion other than the inlet 55d1 in the oil supply passage 55d are blocked by the flow passage forming member 54a together with the upper end portion of the vane back chamber 25. . A lower end portion of the vane back chamber 25 is closed by a flow path forming member 54b.

  A part of the inner wall surface of the oil supply passage 55 c is configured by the left side surface 53 d of the magnetic body 53. In the flow of the lubricating oil in the oil supply passage 55c, the surface 53a of the magnetic body 53 is disposed on the downstream side of the left side surface 53d. In addition, a part of the inner wall surface of the oil supply passage 55 d is configured by the right side surface 53 e of the magnetic body 53. In the flow of the lubricating oil in the oil supply passage 55d, the surface 53a of the magnetic body 53 is disposed on the downstream side of the right side surface 53e.

  Mesh members 56a and 56b are provided in the oil supply passages 55c and 55d, respectively. The mesh members 56a and 56b of this example are arranged on the downstream side of the permanent magnet 51 and the upstream side of the yoke 52 in each of the oil supply passages 55c and 55d. It may be arranged on the downstream side.

  The lubricating oil that has flowed into the oil supply passage 55 c from the inflow port 55 c 1 flows along the left side surface 53 d of the magnetic body 53 and then flows into the vane back chamber 25. Similarly, the lubricating oil flowing into the oil supply passage 55d from the inlet 55d1 flows along the right side surface 53e of the magnetic body 53 and then flows into the vane back chamber 25. As a result, the metal piece 80 mixed in the lubricating oil enters the magnetic field of the magnetic body 53 and is adsorbed to the left side surface 53d or the right side surface 53e, so that the metal piece 80 enters the vane back chamber 25. Can be prevented. Therefore, in the present embodiment, the same effect as in the first embodiment can be obtained. In the present embodiment, since the oil supply passages 55c and 55d are formed in the second cylinder 21, the parts for forming the oil supply passages 55c and 55d can be omitted, and the number of parts can be increased. Can be suppressed.

Embodiment 4 FIG.
A refrigerant compressor according to Embodiment 4 of the present invention will be described. In the third embodiment, the oil supply channels 55c and 55d are configured to extend in parallel along the left side surface 53d and the right side surface 53e of the magnetic body 53, respectively. If the oil supply flow path is configured as follows, it is possible to more reliably prevent the metal piece 80 from entering the vane back chamber 25. Note that components that are not particularly described in this embodiment mode are the same as those in Embodiment Mode 1, and the same functions and configurations are described using the same reference numerals.

  FIG. 11 is a schematic cross-sectional view showing the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment, and is a view showing a cross-section corresponding to FIG. As shown in FIG. 11, the oil supply passage 55 e is formed in the second cylinder 21. The oil supply passage 55 e extends in the tangential direction of the second cylinder 21 perpendicular to the left side surface 53 d (the right side surface in FIG. 11) of the magnetic body 53. A part of the oil supply passage 55e has, for example, a bottomed groove shape formed from the upper surface side of the second cylinder 21. The inlet 55e1 of the oil supply passage 55e is provided upward at the end of the oil supply passage 55e located at the outer peripheral portion of the second cylinder 21. Portions other than the inlet 55e1 in the upper part of the oil supply channel 55e are closed by the channel forming member 54a together with the upper end of the vane back chamber 25. The lower end portion of the vane back chamber 25 is closed by a flow path forming member 54b (not shown in FIG. 11).

  A part of the inner wall surface of the oil supply channel 55 e is configured by the left side surface 53 d of the magnetic body 53. In the flow of the lubricating oil in the oil supply passage 55e, the surface 53a of the magnetic body 53 is disposed on the downstream side of the left side surface 53d. A mesh member 56c is provided in a rounded state on the downstream side of the left side surface 53d of the magnetic body 53 in the oil supply passage 55e.

  The lubricating oil flowing into the oil supply passage 55e from the inflow port 55e1 flows toward the left side surface 53d of the magnetic body 53, collides with the left side surface 53d, and then flows into the vane back chamber 25. Thereby, the metal piece 80 mixed in the lubricating oil passes through the vicinity of the left side surface 53d where the magnetic field generated by the permanent magnet 51 is strong before flowing into the vane back chamber 25. For this reason, the metal piece 80 in the lubricating oil can be more reliably adsorbed to the left side surface 53d. Therefore, in the present embodiment, a higher removal effect of the metal piece 80 than in the third embodiment can be obtained.

Embodiment 5. FIG.
A refrigerant compressor according to Embodiment 5 of the present invention will be described. In the first to fourth embodiments, the mesh members 56a to 56c are arranged on the downstream side of the magnetic body 53 in the flow of the lubricating oil. Even if the mesh member is arranged as described below, the metal piece 80 can be prevented from entering the vane back chamber 25.

  FIG. 12 is a schematic longitudinal sectional view showing the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment. As shown in FIG. 12, the mesh members 56a and 56b of the present embodiment are arranged on the upstream side of the magnetic body 53 in the flow of the lubricating oil in the oil supply passages 55a and 55b. That is, the relatively large metal piece 80 is captured by the mesh members 56a and 56b, and the relatively small metal piece 80 is captured by the upper side surface 53b and the lower side surface 53c of the magnetic body 53. Also according to the present embodiment, since the metal piece 80 can be prevented from entering the vane back chamber 25 as in the first to fourth embodiments, the reliability of the sliding portion of the refrigerant compressor 100 can be improved. The stability of the attractive magnetic force acting on the vane can be improved.

Embodiment 6 FIG.
A refrigerant compressor according to Embodiment 6 of the present invention will be described. In the first to fifth embodiments, the configuration in which the compression operation and the cylinder resting operation are switched depending on the magnitude relationship between the first force and the second force acting on the second vane 24 has been described. The effects similar to those of the first to fifth embodiments can be obtained even in the configuration in which the cylinder resting operation and the compression operation are switched as described below.

  FIG. 13 is a schematic longitudinal sectional view showing the configuration of the refrigerant compressor 100 according to the present embodiment. Note that components that are not particularly described in this embodiment mode are the same as those in Embodiment Mode 1, and the same functions and configurations are described using the same reference numerals.

  As shown in FIG. 13, the refrigerant compressor 100 of the present embodiment connects the pressure switching valve 150 provided in the outflow pipe 6 d of the suction muffler 6 and the compressor discharge pipe 2 and the pressure switching valve 150. And a bypass pipe 160. The pressure switching valve 150 switches the connection destination of the cylinder suction passage 27. When the flow path of the pressure switching valve 150 is switched as shown by the solid line in FIG. 13, the cylinder suction flow path 27 communicates with the outflow pipe 6 d of the suction muffler 6. On the other hand, when the flow path of the pressure switching valve 150 is switched as indicated by the broken line in FIG. 13, the cylinder suction flow path 27 communicates with the bypass pipe 160.

  When the cylinder suction flow path 27 and the outflow pipe 6d of the suction muffler 6 communicate with each other, the low pressure refrigerant is guided to the second cylinder chamber 22 via the suction muffler 6, so that the suction pressure is applied to the distal end portion 24a of the second vane 24. Act. The discharge pressure acts on the rear end 24b of the second vane 24 as in the first embodiment. When the pressing force (first force) acting on the second vane 24 due to the pressure difference between the front end portion 24a and the rear end portion 24b of the second vane 24 exceeds the attractive magnetic force (second force) of the permanent magnet 51, the second The tip 24 a of the vane 24 contacts the second piston 23. Therefore, the operation state of the second compression mechanism 20 is autonomously switched between the cylinder resting operation and the compression operation.

  On the other hand, when the cylinder suction passage 27 and the bypass pipe 160 communicate with each other by switching the pressure switching valve 150, a high-pressure (discharge pressure) refrigerant is guided to the second cylinder chamber 22 through the bypass pipe 160. Thereby, discharge pressure acts on both the front-end | tip part 24a and the rear-end part 24b of the 2nd vane 24, and 1st force is less than 2nd force. For this reason, the rear end portion 24b of the second vane 24 is attracted and held by the magnetic body 53, and the second compression mechanism 20 is in a cylinder resting operation state.

  As described above, in the present embodiment, although the method for switching between the compression operation and the cylinder resting operation is different from that in the first embodiment, the method is implemented in that the vane back chamber 25 and the lubricating oil storage unit 3a communicate with each other. This is the same as the first embodiment. Therefore, also in the present embodiment, since the metal piece 80 mixed in the lubricating oil can be prevented from entering the vane back chamber 25, the reliability of the sliding portion of the refrigerant compressor 100 can be improved and the compression can be performed. Operation and non-cylinder operation can be switched stably.

Embodiment 7 FIG.
A vapor compression refrigeration cycle apparatus according to Embodiment 7 of the present invention will be described. The refrigerant compressor 100 according to the first to sixth embodiments is used in, for example, a vapor compression refrigeration cycle apparatus as shown below.

  FIG. 14 is a refrigerant circuit diagram showing the configuration of the vapor compression refrigeration cycle apparatus 500 according to the present embodiment. As shown in FIG. 14, the vapor compression refrigeration cycle apparatus 500 includes the refrigerant compressor 100 shown in any of Embodiments 1 to 6, and the radiator 300 that radiates heat from the refrigerant compressed by the refrigerant compressor 100. An expansion mechanism 200 that expands the refrigerant that has flowed out of the radiator 300 and an evaporator 400 that absorbs heat from the refrigerant that has flowed out of the expansion mechanism 200 are provided.

  As in the vapor compression refrigeration cycle apparatus 500 according to the present embodiment, by including the refrigerant compressor 100 shown in any of the first to sixth embodiments, energy is saved in an actual load operation while improving reliability. The performance can be improved.

  As described above, the refrigerant compressor 100 according to the first to sixth embodiments includes the sealed container 3 storing the lubricating oil, and the first compression mechanism 10 and the second compression mechanism 20 housed in the sealed container 3. And. The first compression mechanism 10 includes a first cylinder 11 having a first cylinder chamber 12, a first piston 13 that rotates eccentrically in the first cylinder chamber 12, and a tip portion 14 a that contacts the first piston 13. A first vane 14 that partitions the first cylinder chamber 12 into a plurality of spaces, a vane groove 19 that is formed in the first cylinder 11 and reciprocally accommodates the first vane 14, and a vane groove of the first cylinder 11. And a vane back chamber 15 that is formed on the outer peripheral side of the housing 19 and accommodates the rear end portion 14 b of the first vane 14. The second compression mechanism 20 includes a second cylinder 21 having a second cylinder chamber 22, a second piston 23 that rotates eccentrically in the second cylinder chamber 22, and a tip 24 a that contacts the second piston 23. A second vane 24 that partitions the second cylinder chamber 22 into a plurality of spaces, a vane groove 29 that is formed in the second cylinder 21 and reciprocally accommodates the second vane 24, and a vane groove of the second cylinder 21. 29 and a vane back chamber 25 that is formed on the outer peripheral side of the second vane 24 and accommodates the rear end portion 24 b of the second vane 24. The second compression mechanism 20 includes a compression operation in which the refrigerant is compressed in a state where the tip 24a of the second vane 24 is in contact with the second piston 23, and the tip 24a of the second vane 24 is separated from the second piston 23. And a cylinder resting mechanism 50 for switching between a cylinder resting operation in which the refrigerant is not compressed. The cylinder resting mechanism 50 includes a magnetic body 53 that generates an attractive magnetic force that attracts the second vane 24 in a direction away from the second piston 23. The magnetic body 53 includes a first surface (for example, a surface 53 a) that faces the vane back chamber 25 and faces the rear end portion 24 b of the second vane 24. In the second compression mechanism 20, the lubricating oil stored in the hermetic container 3 is supplied to a second surface (for example, an upper side surface 53b, a lower side surface 53c, a direction different from the first surface of the magnetic body 53). Oil supply passages (for example, oil supply passages 55a, 55b, 55c, 55d, and 55e) that supply the vane back chamber 25 are formed along the left side surface 53d and the right side surface 53e). A part of the inner wall surface of the oil supply passage is constituted by the second surface of the magnetic body 53 (for example, the upper side surface 53b, the lower side surface 53c, the left side surface 53d, and the right side surface 53e).

  According to this configuration, since the metal piece 80 mixed in the lubricating oil can be captured by the second surface of the magnetic body 53 before flowing into the vane back chamber 25, the metal piece 80 is captured by the vane back chamber 25. Intrusion can be prevented. Therefore, the reliability of the sliding part can be improved. Further, according to this configuration, since the metal piece 80 can be captured before the metal piece 80 reaches the surface 53a of the magnetic body 53, it is possible to prevent variation in the attractive magnetic force acting on the second vane 24. . Therefore, it is possible to stably switch between the compression operation and the idle cylinder operation.

  In the refrigerant compressor 100 according to Embodiments 1 to 6, mesh members 56a, 56b, and 56c may be provided on the downstream side of the second surface in the oil supply passage.

  According to this configuration, since the metal piece 80 that could not be captured by the second surface of the magnetic body 53 can be captured by the mesh members 56a, 56b, and 56c, the metal piece 80 enters the vane back chamber 25. Can be prevented more reliably.

  In the refrigerant compressor 100 according to the first to sixth embodiments, the mesh members 56a, 56b, and 56c are formed using a magnetic material, and may be in contact with the magnetic body 53.

  According to this configuration, since the mesh members 56a, 56b, and 56c can be magnetized, the effect of capturing the metal piece 80 by the mesh members 56a, 56b, and 56c can be further enhanced.

  In the refrigerant compressor 100 according to Embodiments 1 to 6, mesh members 56a and 56b may be provided on the upstream side of the second surface in the oil supply passage.

  According to this configuration, the metal piece 80 can be more reliably prevented from entering the vane back chamber 25.

  Further, in the refrigerant compressor 100 according to the first to sixth embodiments, the second compression mechanism 20 is provided to face the second surface of the magnetic body 53 and is provided with another part of the inner wall surface of the oil supply passage. You may further have the flow-path formation member 54a, 54b to comprise. In the refrigerant compressor 100 according to Embodiments 1 to 6, the flow path forming members 54a and 54b may be formed using a nonmagnetic material.

  According to this configuration, it is possible to prevent the magnetic field from the magnetic body 53 from flowing to the flow path forming members 54a and 54b, and thus it is possible to prevent the attractive magnetic force that attracts the second vane 24 from decreasing.

  In the refrigerant compressor 100 according to Embodiments 1 to 6, the other part of the inner wall surface of the oil supply passage may be configured by the second cylinder 21.

  Further, the vapor compression refrigeration cycle apparatus 500 according to the seventh embodiment includes the refrigerant compressor 100 according to the first to sixth embodiments, the radiator 300 that radiates heat from the refrigerant compressed by the refrigerant compressor 100, and An expansion mechanism 200 that expands the refrigerant that has flowed out of the radiator 300 and an evaporator 400 that absorbs heat from the refrigerant that has flowed out of the expansion mechanism 200 are provided.

  According to this configuration, it is possible to improve the energy saving performance in the actual load operation while improving the reliability of the vapor compression refrigeration cycle apparatus 500.

Other embodiments.
The present invention is not limited to the above embodiment, and various modifications can be made.
For example, in the above-described embodiment, a vertical type refrigerant compressor is taken as an example, but the present invention is also applicable to a horizontal type refrigerant compressor.

  Moreover, in the said embodiment, although the structure provided with the mesh member in the oil supply flow path was mentioned as an example, a mesh member can also be abbreviate | omitted.

  In addition, the above embodiments and modifications can be implemented in combination with each other.

  2 Compressor discharge pipe, 3 Airtight container, 3a Lubricating oil storage part, 4 Intermediate partition plate, 5 Drive shaft, 5a Long shaft part, 5b Short shaft part, 5c, 5d Eccentric pin shaft part, 5e Intermediate shaft part, 6 Suction Muffler, 6a Inflow pipe, 6b Container, 6c, 6d Outflow pipe, 7 Internal space, 8 Electric motor, 8a Rotor, 8b Stator, 10 1st compression mechanism, 11 1st cylinder, 12 1st cylinder chamber, 12a Suction chamber , 12b Compression chamber, 13 First piston, 14 First vane, 14a Front end, 14b Rear end, 15 Vane back chamber, 17 Cylinder suction flow path, 18 Discharge port, 19 Vane groove, 20 Second compression mechanism, 21 2nd cylinder, 22 2nd cylinder chamber, 23 2nd piston, 24 2nd vane, 24a tip part, 24b rear end part, 25 vane back chamber, 27 cylinder suction flow path, 28 discharge port, 2 Vane groove, 40 compression spring, 50 cylinder resting mechanism, 51 permanent magnet, 52 yoke, 53 magnetic body, 53a surface, 53b upper side surface, 53c lower side surface, 53d left side surface, 53e right side surface, 54a, 54b flow path forming member, 55a, 55b, 55c, 55d, 55e Oil supply passage, 55a1, 55b1, 55c1, 55d1, 55e1 Inlet, 56a, 56b, 56c Mesh member, 60 First support member, 60a Bearing part, 60b Flange part, 63 Discharge muffler , 70 second support member, 70a bearing portion, 70b flange portion, 73 discharge muffler, 80 metal piece, 99 compression mechanism, 100 refrigerant compressor, 150 pressure switching valve, 160 bypass pipe, 200 expansion mechanism, 300 radiator, 400 Evaporator, 500 Vapor compression refrigeration cycle equipment.

Claims (8)

A sealed container storing lubricating oil;
A plurality of compression mechanisms housed in the sealed container,
Each of the plurality of compression mechanisms is
A cylinder having a cylinder chamber;
A piston that rotates eccentrically in the cylinder chamber;
A vane having a tip portion in contact with the piston and partitioning the cylinder chamber into a plurality of spaces;
A vane groove formed in the cylinder and reciprocally storing the vane;
A vane back chamber that is formed on the outer peripheral side of the vane groove of the cylinder and accommodates a rear end portion of the vane, and
At least one of the plurality of compression mechanisms includes a compression operation in which the refrigerant is compressed in a state where the tip of the vane is in contact with the piston, and the tip of the vane is separated from the piston. It has a cylinder resting mechanism that switches between cylinder resting operation without compression of
The cylinder resting mechanism includes a magnetic body that generates an attractive magnetic force that attracts the vane in a direction away from the piston.
The magnetic body includes a first surface facing the vane back chamber and facing a rear end portion of the vane,
The at least one compression mechanism supplies lubricating oil stored in the hermetic container to the vane back chamber along a second surface of the magnetic body whose direction is different from that of the first surface. An oil supply passage is formed,
A refrigerant compressor in which a part of the inner wall surface of the oil supply passage is configured by the second surface.   The refrigerant compressor according to claim 1, wherein a mesh member is provided on a downstream side of the second surface in the oil supply passage.   The refrigerant compressor according to claim 2, wherein the mesh member is formed using a magnetic material and is in contact with the magnetic body.   The refrigerant compressor according to claim 1, wherein a mesh member is provided on the upstream side of the second surface in the oil supply passage.   The said at least 1 compression mechanism is further provided with the flow-path formation member which comprises the other part of the inner wall face of the said oil supply flow path provided facing the said 2nd surface. A refrigerant compressor according to claim 1.   The refrigerant compressor according to claim 5, wherein the flow path forming member is formed using a nonmagnetic material.   The refrigerant compressor according to any one of claims 1 to 6, wherein another part of the inner wall surface of the oil supply passage is configured by the cylinder.   The refrigerant compressor according to any one of claims 1 to 7, a radiator that radiates heat from the refrigerant compressed by the refrigerant compressor, an expansion mechanism that expands the refrigerant that has flowed out of the radiator, A vapor compression refrigeration cycle apparatus comprising: an evaporator that absorbs heat from the refrigerant flowing out of the expansion mechanism.

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