JP2008138534A - Closed rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To increase the amount of oil supply to the vane sliding part of a rotary compressor having a plurality of compressor sections and to ensure reliability, in a closed two-stage rotary compressor. <P>SOLUTION: This closed two-stage rotary compressor 1 is provided with, in a sealed container, an electric motor, a crankshaft driven by the electric motor and having a plurality of eccentric parts, the plurality of compressor sections driven by the eccentric parts, and a plurality of closing members for closing the plurality of compressor sections in a crankshaft direction. The compressor sections each have a compression chamber having a cylinder, a roller arranged in the cylinder and rotatively driven by the eccentric parts, two closing members axially closing the cylinder, and a vane extending from the periphery of the roller and going in and out from a storage part arranged in the cylinder according to the eccentric movement of the roller. A communication space communicating with a space in the sealed container is arranged to at least one of two closing members for closing the compressor sections, and is arranged in a part opposed the storage part for the vane. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a hermetic rotary compressor having a plurality of compressor sections.

  As a hermetic rotary compressor having a plurality of compressor sections, a structure disclosed in Japanese Patent Laid-Open No. 60-128990 (Patent Document 1) is known.

  In this compressor, first, the refrigerant gas is compressed by a first compressor portion provided in the sealed container. The refrigerant gas compressed by the first compressor unit is compressed by the second compressor unit through piping outside the compressor. The refrigerant gas compressed by the second compressor section is sent to another configuration of the refrigeration cycle through a pipe.

JP 60-128990 A

  In the hermetic rotary compressor of Patent Document 1, each compressor section includes a cylinder and a vane for partitioning a compression chamber formed in the cylinder.

  The vane slides with a roller that moves eccentrically in the cylinder while entering and exiting from a storage portion provided in the cylinder. While the cylinder and the roller slide, a space is formed between two plate-like cylinder closing members that close the cylinder in the axial direction. Thus, the vane partitions a space formed by the cylinder and the roller into a suction chamber and a compression chamber.

  A vane that enters and exits a storage portion provided in the cylinder includes a sliding surface that slides with a plate-like member that closes the cylinder in the axial direction. The sliding surface of the vane does not open to the refrigerating machine oil present in the sealed container.

  Conventionally, when a vane enters and exits into a compression chamber supplied with refrigerating machine oil, the refrigerating machine oil adhering to the vane is taken into the vane storage portion and the sliding surface with the cylinder closing member is lubricated.

  However, with the indirect supply of refrigerating machine oil accompanying the forward and backward movement of the vane, the sliding portion between the vane and the plate-like member is likely to be insufficiently lubricated, causing a problem that the reliability of the rotary compressor is reduced. It was.

  Furthermore, as a problem peculiar to a rotary compressor having a plurality of compressor parts, when supplying oil (referred to as differential pressure oil supply) by the differential pressure between the pressure in the sealed container and each compressor part, the high pressure side compressor part is There may be cases where the required amount of oil cannot be provided by refueling with differential pressure.

The pressure (suction pressure) of the refrigerant gas sucked by the high-pressure side compressor portion is an intermediate pressure Pm compressed by the low-pressure side compressor portion. The relationship with the suction pressure Ps of the refrigerant gas sucked by the low-pressure compressor section is Pm> Ps.

  The discharge pressure Pd of the high-pressure compressor section discharged into the closed container becomes the pressure applied to the refrigeration oil in the closed container. In the case of differential pressure supply, the suction pressure Ps of the low-pressure compressor section and the pressure Pd applied to the refrigeration oil. (Pd−Ps) is a pressure difference sufficient to supply the differential pressure to the low-pressure compressor section.

However, the pressure difference (Pd−Pm) between the pressure Pd applied to the refrigerating machine oil and the suction pressure Pm of the high-pressure side compressor section is small, which may lead to insufficient oil supply.

  Further, as a problem peculiar to the two-stage rotary compressor, there has been a problem that the low-pressure side compressor portion causes wear of the vane sliding portion due to high dilution of the refrigerating machine oil when the liquid refrigerant is compressed.

  Depending on the conditions of the refrigeration cycle to which the compressor is connected, there may be a case where liquid refrigerant returns to the compressor instead of gas refrigerant (the refrigerant sucks liquid refrigerant). In this case, the liquid refrigerant is sucked into the low pressure side compressor portion of the two-stage rotary compressor, and the liquid refrigerant enters not only the compression chamber but also the vane sliding portion. Then, the refrigerating machine oil adhering to the liquid refrigerant is dissolved, and the amount of the refrigerating machine oil attached to the sliding surface is reduced.

  An object of the present invention is to improve the reliability of a hermetic rotary compressor having a plurality of compressor sections.

  In order to achieve the above-mentioned object, a hermetic rotary compressor according to the present invention is driven by an electric motor, a crankshaft driven by the electric motor and having a plurality of eccentric parts, and the eccentric part. A plurality of compressor units and a plurality of closing members that close the plurality of compressor units in the crankshaft direction. The compressor unit is disposed in the cylinder and is rotationally driven by the eccentric unit. And two closing members for closing the cylinder in the axial direction, and a vane extending to the outer periphery of the roller and entering and exiting a storage portion provided in the cylinder according to the eccentric motion of the roller. A compression chamber having a communication space provided in at least one of the two closing members for closing the compressor portion and communicating with the space in the hermetic container at a portion facing the storage portion of the vane A.

  The closing member may include a hole portion through which the crankshaft passes and a bearing portion continuous with the hole portion.

  Further, the communication space provided in the closing member may be a recess facing the vane.

  Further, the closing member may be a partition plate that partitions the compression chambers.

  Furthermore, the communication space may have any one planar structure of an arc shape, a trapezoidal shape, or a rectangular shape.

  You may have the intermediate discharge space in which the gas compressed in one compression chamber is discharged, and the intermediate communication path which connects this intermediate discharge space and the suction port of the other compression chamber.

  ADVANTAGE OF THE INVENTION According to this invention, the amount of oil supply to the vane sliding part of the rotary compressor which has a some compressor part can be increased, and the sealed rotary compressor which ensured reliability can be provided.

  A hermetic two-stage rotary compressor according to an embodiment of the present invention will be described with reference to the drawings. Although the present embodiment will be described using an example provided with two compressor sections, it goes without saying that the present invention is not limited to two. In FIG. 1, the hermetic two-stage rotary compressor 1 includes a hermetic container 13 including a bottom portion 21, a lid portion 12, and a trunk portion 22.

  An electric motor 14 having a stator 7 and a rotor 8 is provided at the upper part in the sealed container 13. The outer periphery of the stator 7 is fixed to the hermetic container 13, and the rotor 8 is fixed to the outer periphery of the upper portion of the crankshaft 2 and is rotatably disposed in the stator 7.

  By energizing the stator 7, the rotor 8 rotates, and the crankshaft 2 is rotationally driven accordingly.

  A compressor part including a low-pressure side compressor part 20a and a high-pressure side compressor part 20b is provided in the lower part of the hermetic container 13. The low pressure side compressor part 20a and the high pressure side compressor part 20b divide the pressure space of the working fluid compressed by each compressor part by using a partition plate 15 therebetween.

  A blocking member that closes the pressure space in the direction of the crankshaft 2 with respect to the low pressure side compressor portion 20a and the high pressure side compressor portion 20b together with the partition plate 15 is provided on the motor 14 side of the high pressure side compressor portion 20b. The side end plate 9a and the low pressure side end plate 19b provided on the opposite side of the low pressure side compressor portion 20a from the high pressure side compressor portion 20b are also provided.

  The low-pressure side compressor unit 20a and the high-pressure side compressor unit 20b are driven by the crankshaft 2, and compress the gas refrigerant that is the working fluid.

  The crankshaft 2 connected to the electric motor 14 has two eccentric portions 5a and 5b. The eccentric portion 5a is a low pressure side eccentric portion, and the eccentric portion 5b is a high pressure side eccentric portion. The crankshaft 2 is pivotally supported by the main bearing 9 and the auxiliary bearing 19a.

  The main bearing 9 is installed on the upper side of the high pressure side eccentric part 5b, and the sub bearing 19a is installed on the lower side of the low pressure side eccentric part 5a.

  Next, the low-pressure side compressor unit 20a will be described. The low-pressure side compressor unit 20a is disposed in the cylinder chamber of the low-pressure side cylinder 10a having a circular cylinder chamber at the center and the low-pressure side eccentric portion 5a of the crankshaft 2 is eccentrically rotated. The side roller 11a and the upper side in the axial direction of the low pressure side cylinder 10a are closed, and the partition plate 15 provided between the low pressure side cylinder 10a and the high pressure side cylinder 10b is opposite to the partition plate 15 with respect to the low pressure side cylinder 10a. A low-pressure side end plate 19b disposed on the side, following the eccentric rotation of the low-pressure side roller 11a, and coming into and out of a low-pressure side cylinder vane storage portion 41a provided in the low-pressure side cylinder 10a; It has a low-pressure side compression chamber 23a. The partition plate 15 is shared by the low-pressure compressor unit 20a and the high-pressure compressor unit 20b. In the present embodiment, the low-pressure side end plate 19b is a part of the auxiliary bearing 19a.

  Among the components constituting the low-pressure side compression chamber 23a, the relationship between the low-pressure side cylinder 10a and the low-pressure side roller 11a will be described first. The low-pressure side roller 11a is a cylindrical part having an outer diameter smaller than the diameter of the cylinder chamber of the low-pressure side cylinder 10a. While the outer peripheral surface of the low-pressure side roller 11a slides with the inner peripheral surface of the low-pressure side cylinder 10a constituting the cylinder chamber of the low-pressure side cylinder 10a, the low-pressure side roller 11a is passed through the refrigerating machine oil supplied into the cylinder chamber. Rotates eccentrically in the cylinder chamber.

  Next, the relationship between the low-pressure side roller 11a and the low-pressure side vane 18a will be described. The low-pressure side roller 11a and the low-pressure side vane 18a may be provided integrally or separately. In the present embodiment, the case where they are provided separately will be described.

  The low-pressure side vane 18a, which is a flat plate-like member, moves forward and backward so as to always contact the outer peripheral surface of the low-pressure side roller 11a that rotates eccentrically in accordance with the rotation of the low-pressure side eccentric portion 5a. Therefore, the low pressure side vane 18a is given a biasing force by a low pressure side coil spring 48a from the back surface (the surface opposite to the surface in contact with the low pressure side roller 11a).

  The low pressure side vane 18a follows the eccentric rotation of the low pressure side roller 11a, and moves in and out of the low pressure side cylinder vane storage part 41a, so that the axial direction is closed by the partition plate 15 and the low pressure side end plate 19b. The low pressure side compression chamber 23a formed by the outer peripheral surface of the low pressure side roller 11a and the inner peripheral surface of the low pressure side cylinder 10a is divided into a compression space and a suction space in accordance with the rotation of the crankshaft 2.

  The contact between the low-pressure side vane 18a and the low-pressure side roller 11a will be described in more detail. The surface of the low-pressure side vane 18a facing the low-pressure side roller 11a is in contact with the low-pressure side roller 11a through refrigerating machine oil. . Due to the lubricating and sealing action of the refrigerating machine oil, the wear of both is suppressed and leakage of the compressed refrigerant gas from the compression space is suppressed.

A suction port 25a and a discharge port 42 are provided on the inner peripheral surface forming the cylinder chamber of the low pressure side cylinder 10a at a position close to the low pressure side cylinder vane storage portion 41a of the low pressure side vane 18a. The suction port 25a and the discharge port 42 are disposed with the low-pressure vane 18a interposed therebetween.

  The center of the cylinder chamber of the low-pressure side cylinder 10a coincides with the rotation center 2a of the crankshaft 2.

  The outer periphery of the low-pressure side cylinder 10 a has at least one side portion provided so as to be in contact with the inner peripheral surface of the sealed container 13. In this embodiment, a pair of side portions are provided at positions that are mutually targeted.

  The suction port 25a, the discharge port 42, and the low pressure side cylinder vane storage portion 41a provided in the low pressure side cylinder 10a are provided in one of the side portions. In particular, the suction port 25a is provided from the outside of the sealed container 13 as a working fluid. Is provided on the outer peripheral portion of the low-pressure side cylinder 10 a and on the side portion reaching the inner wall of the sealed container 13.

The refrigerant gas compressed in the low pressure side compression chamber 23a of the low pressure side compressor unit 20a is discharged out of the low pressure side compression chamber 23a from the discharge port 42 of the low pressure side compression chamber 23a. The discharge port 42 communicates with a discharge port 26a provided in the low-pressure side end plate 19b, and the refrigerant gas compressed in the low-pressure side compression chamber 23a is discharged from the discharge port 26a to the intermediate discharge space 33.

  A discharge valve 28a that opens the discharge port 26a at a predetermined intermediate pressure Pm is provided at the outlet of the discharge port 26a. Accordingly, the refrigerant gas is discharged into the intermediate discharge space 33 at the intermediate pressure Pm. The refrigerant gas having the intermediate pressure Pm is guided from the intermediate discharge space 33 to the intermediate flow path connecting pipe 30 drawn out of the compressor.

  The intermediate discharge space 33 includes an intermediate container 19 that forms a concave space surrounded by the auxiliary bearing 19a, the low-pressure side end plate 19b, and the outer wall portion 19c, and a cover 35 that closes an opening that opens below the intermediate container 19. Has been. As in the present embodiment, the intermediate container 19 may be provided by integrally forming the auxiliary bearing 19a, the low-pressure side end plate 19b, and the outer wall portion 19c with the same member.

  Next, the high-pressure side compressor unit 20b will be described. The basic components are the same as those of the low-pressure compressor unit 20a.

  First, the high-pressure side compressor portion 20b is eccentric by the high-pressure side cylinder 10b having a circular cylinder chamber formed in the center and the high-pressure side eccentric portion 5b of the crankshaft 2 that is disposed in the cylinder chamber of the high-pressure side cylinder 10b. A partition plate 15 provided between the low-pressure side cylinder 10a and the high-pressure side cylinder 10b by closing the axially lower side of the high-pressure side roller 11b and the high-pressure side cylinder 10b (on the low-pressure side compressor portion 20a side). And a high pressure side end plate 9a that closes the side opposite to the axial partition plate 15 of the high pressure side cylinder 10b, in contact with the eccentric rotation of the high pressure side roller 11b, and a storage section provided in the high pressure side cylinder 10b And a high-pressure side compression chamber 23b composed of a high-pressure side vane 18b entering and exiting from 41b.

  On the inner peripheral surface forming the cylinder chamber of the high pressure side cylinder 10b, a discharge port 43 is provided in a portion close to the high pressure side vane 18b. Further, a suction port 25 is also provided in a portion adjacent to the high pressure side vane 18b, and the suction port 25 and the discharge port 43 are arranged with the high pressure side vane 18b interposed therebetween.

  The outer periphery of the high-pressure side cylinder 10 b has at least one side portion provided so as to coincide with the inner peripheral surface of the sealed container 13. In this embodiment, a pair of side portions are provided at positions that are mutually targeted.

  When the suction port 25a connected to the intermediate flow path connecting pipe 30 routed from the inside of the compressor to the outside and the storage portion 41b of the high pressure side vane 18b reach close to the inner wall of the hermetic container 13, the intermediate flow path connecting pipe Since it is easy to connect to 30 or a depth for advancing and retracting is required, it is provided on one of the side portions.

  The center of the cylinder chamber of the high-pressure side cylinder 10b coincides with the rotation center 2a of the crankshaft 2. The cylinder chamber of the low-pressure side cylinder 10a and the cylinder chamber of the high-pressure side cylinder 10b have the same radial dimension and different height (axial) dimensions. The height dimension of the cylinder chamber of the low pressure side cylinder 10a is larger than the height dimension of the cylinder chamber of the high pressure side cylinder 10b.

  The high-pressure side roller 11b is a cylindrical part having an outer diameter smaller than the diameter of the cylinder chamber of the high-pressure side cylinder 10b. While the outer peripheral surface of the high-pressure roller 11b slides on the inner peripheral surface of the high-pressure cylinder 10b constituting the cylinder chamber, the high-pressure roller 11b rotates eccentrically in the cylinder chamber via the refrigerating machine oil supplied into the cylinder chamber. . A high pressure side compression chamber 23b is formed between the outer peripheral surface of the high pressure side roller 11b and the inner peripheral surface constituting the cylinder chamber of the high pressure side cylinder 10b.

  The high-pressure side end plate 9a is composed of the same member integrally with the main bearing 9, but may be formed integrally by combining separate members.

  In the present embodiment, the high pressure side vane 18b is a flat plate member that is separate from the high pressure side roller 11b. The high-pressure side vane 18b moves forward and backward from the high-pressure side cylinder vane storage portion 41b so as to always contact the outer peripheral surface of the high-pressure side roller 11b that rotates eccentrically with the rotation of the high-pressure side eccentric portion 5b. Therefore, the high pressure side vane 18b is given a biasing force by a high pressure side coil spring 48b from the back surface (the surface opposite to the surface in contact with the high pressure side roller 11b). The high pressure side vane 18b contacts the high pressure side roller 11b, thereby dividing the high pressure side compression chamber 23b into a compression space and a suction space.

  The high pressure side end plate 9a is provided with a discharge port 26b communicating with the discharge port 43 of the high pressure side compression chamber 23b. A discharge valve 28b that opens at a predetermined discharge pressure Pd is provided on the discharge side of the discharge port 26b. The gas refrigerant compressed in the high-pressure side compression chamber 23b is discharged from the discharge port 43 through the discharge port 26b, through the discharge valve 28b, and into the sealed container 13. The high-pressure side end plate 9a has an outer shape whose outer peripheral portion substantially coincides with the inner periphery of the sealed container 13, and is fixed to the sealed container 13 by spot welding, for example.

  The low-pressure compressor unit 20a and the high-pressure compressor unit 20b described above are stacked and fixed. Specifically, the cover 35, the low-pressure side end plate 19b, the low-pressure side cylinder 10a, the partition plate 15, the high-pressure side cylinder 10b, and the high-pressure side end plate 9a are stacked in this order from the bottom, and the low-pressure side cylinder. The plane angle position (the angular position in the rotation direction of the crankshaft 2) of the vane storage part 41a of 10a and the vane storage part 41b of the high-pressure side cylinder 10b is made the same through the bolt 36 from the lower side of the cover 35. Is done.

  Next, the compression operation of the hermetic two-stage rotary compressor of this embodiment will be described with reference to FIGS. 1 and 2. The arrows in FIGS. 1 and 2 indicate the flow of the gas refrigerant.

  The low-pressure Ps gas refrigerant supplied through the pipe 31 connected to the low-pressure region of the refrigeration cycle is sucked into the low-pressure side compression chamber 23a through the suction port 25a connected to the pipe 31.

  As the low pressure roller 11a rotates eccentrically, the amount of refrigerant gas sucked increases as the suction space of the low pressure compression chamber 23a increases, and the eccentric rotation of the low pressure roller 11a advances, so that the low pressure roller 11a passes through the suction port 25a. When passing, the suction space for sucking in the low-pressure refrigerant gas is changed to the compression space.

  When the eccentric rotation of the low-pressure side roller 11a advances and the pressure in the compression space rises to the intermediate pressure Pm, the discharge valve 28a that opens when the pressure in the low-pressure side compression chamber 23a reaches a preset pressure opens, The gas refrigerant having the pressure Pm is discharged into the intermediate discharge space 33 communicating with the discharge port 26a.

  The intermediate discharge space 33 is a space isolated from the sealed space 29 in the sealed container 13 by the intermediate container 19 and the cover 35, and the internal pressure thereof is basically the intermediate pressure Pm.

  The gas refrigerant having the intermediate pressure Pm discharged from the discharge port 26a is discharged into the intermediate discharge space 33, and then passes through the intermediate flow passage connecting pipe 30 extending from the discharge port 26c to the suction passage 25b, and then the high pressure side compressor unit 20b. Into the compression chamber 23b.

The gas refrigerant having the intermediate pressure Pm sucked into the high pressure side compression chamber 23b is compressed to a predetermined high pressure Pd by the eccentric rotation of the high pressure side roller 11b. When the discharge valve 28b that opens when the pressure in the compression chamber 23b reaches a preset pressure opens at high pressure Pd, the gas refrigerant is discharged from the discharge port 26b to the sealed space 29 that is the internal space of the sealed container 13. The gas refrigerant discharged into the sealed space 29 passes through the gap of the electric motor 14 and is discharged from the discharge pipe 27.

  Next, refueling to the vane provided in each compressor unit will be described. Although the operating pressure is different between the low pressure side vane 18a and the high pressure side vane 18b, the basic oil supply structure does not change, so the low pressure side vane 18a will be mainly described.

The low pressure side vane 18a slides with the low pressure side cylinder 10a each time it enters and exits the low pressure side cylinder vane storage portion 41a, and also slides with the partition plate 15 and the low pressure side end plate 19b that close the axial direction of the low pressure cylinder 10a. . Therefore, oil must be supplied to form an oil film on each sliding part.

  In the low-pressure side compressor section 20a, the sliding portion in the low-pressure side compression chamber 23a includes the low-pressure side roller 11a in addition to the above-described sliding of the low-pressure side vane 18a. The low pressure side eccentric portion 5a, the low pressure side roller 11a and the low pressure side vane 18a, the low pressure side roller 11a and the partition plate 15, and the low pressure side roller 11a and the low pressure side end plate 19b slide with each other.

  The refrigerating machine oil is fed into the low pressure side compressor section 20a through the oil passage of the crankshaft 2 (not shown), sucking the refrigerating machine oil from the oil reservoir below the hermetic container 13, and inside the low pressure side roller 11a. The refrigerating machine oil is supplied to the low pressure side eccentric portion 5a of the crankshaft 2.

The refrigerating machine oil supplied to the low-pressure side eccentric portion 5a brings an oil film on the sliding surface with the low-pressure side roller 11a, and further, the crankshaft 2 rotates to cause the low-pressure side roller 11a to perform an eccentric motion. The refrigerating machine oil enters the low-pressure side compression chamber 23a through the gaps between 11a, the partition plate 15 and the low-pressure side end plate 19b. The entered refrigerating machine oil adheres to the inner wall of the low-pressure side compression chamber 23a due to the eccentric rotation of the low-pressure side roller 11a and floats as particles in the low-pressure side compression chamber 23a.

  Since the low-pressure side vane 18a moves back and forth in the radial direction of the crankshaft 2, the surface exposed to the low-pressure side compression chamber 23a is transmitted through the inner wall of the low-pressure side compression chamber 23a and the low-pressure side roller 11a, or floats particles. As the refrigerator oil adheres, an oil film of the refrigerator oil is formed. And when entering into the groove-like low pressure side cylinder vane storage part 41a of the low pressure side cylinder 10a, the side surface to which the refrigerating machine oil adheres can ensure lubrication and sealing action.

  However, the surface of the low pressure side vane 18a that slides facing the low pressure side end plate 19b, which is a part of the partition plate 15 and the auxiliary bearing 19a, is difficult to attach the refrigerating machine oil.

  In addition, depending on the operating conditions of the compressor, the low-pressure compressor unit 20a may suck the refrigerant in the liquid state and discharge it in the liquid state. In such a case, a portion of the oil film in contact with the liquid refrigerant is removed, and the refrigerant is gasified and is not discharged, so the formation of a new oil film is delayed. For this reason, in particular, the closer to the end of the low-pressure vane 18a, which is the back of the low-pressure side cylinder vane storage portion 41a provided in the low-pressure cylinder 10a, the more oil is not supplied from the low-pressure side compression chamber 23a.

  The same applies to the oil supply to the high-pressure side vane 18b of the high-pressure side compressor unit 20b. However, in the high-pressure side compressor unit 20b, the discharge pressure Pd in the sealed container 13 and the pressure of the gas refrigerant sucked by the high-pressure side compressor unit 20b. When the differential pressure with respect to (intermediate pressure Pm) is small, sufficient refrigeration oil is not supplied into the high-pressure side compression chamber 23b, and a necessary oil film is not formed on the sliding surface of the high-pressure side vane 18b.

  Therefore, in this embodiment, at least one of the plate-like members that axially close the cylinder and the vane storage portion is hermetically sealed so that the vane storage portion provided in the cylinder communicates with the space in the sealed container. A communication passage communicating with the space in the container 13 was provided. This communication path is provided so as to be connected to a vane storage portion radially outward with respect to the crankshaft. The relationship between the communication path and the vane is that a part of the portion that slides with the plate member of the vane is connected to the communication path on the outer peripheral side of the vane storage part at the position where the vane has completely entered the vane storage part Can come into contact with the refrigerating machine oil.

  FIG. 3 is a cross-sectional view of the high-pressure side end plate 9a as viewed from below (in the direction of arrows XX). The crankshaft 2 penetrates at the center of the high-pressure side end plate 9a, and the bolt 36 penetrates.

  In FIG. 3, the high-pressure side end plate 9a has a surface facing the high-pressure side cylinder 10b. Of the facing surface, the high-pressure side vane 18b moves, and the end of the high-pressure side cylinder vane storage portion 41b. A concave portion 44a serving as a communication passage communicating with the space in the sealed container 13 is provided in the high-pressure side end plate 9a at a portion facing the portion. As shown in FIG. 1, the vane storage portion 41 b that stores the high-pressure vane 18 b and the recess 44 a communicate with each other. The recess 44a forms a space from the vane storage part 41b to the side part storing the high-pressure side coil spring 48b between the high-pressure side cylinder 10b and the high-pressure side end plate 9a. To the vane storage portion 41b.

  In a state where the high-pressure side vane 18b is pushed into the vane storage portion 41b, the high-pressure side vane 18b faces the high-pressure side end plate recess 44a. In FIG. 3, the high-pressure side end plate recess 44a has a substantially arcuate planar shape.

In FIG. 4, an oil groove 44 b that is recessed in a substantially arc shape in the radial direction of the partition plate 15 (penetrated in the thickness direction) causes the radially outer end of the high-pressure side cylinder vane storage portion 41 b to enter the sealed container 13. It has a communication path that communicates and opens. In FIG. 4, the vane storage portion 41b is opened to the extent that the high-pressure side vane 18b slides.

  The high pressure side vane 18b is driven in the radial direction by the high pressure side roller 11b driven to rotate by the high pressure side eccentric portion 5b, and the high pressure side end plate side surface 18c and the high pressure side of the high pressure side vane are driven by the high pressure side end plate recess 44a and the oil groove 44b. Since the vane partition plate side surface 18d can be opened to the refrigerating machine oil 47 interposed in the hermetic container, the high pressure side compressor unit 20b can be supplied with oil and the reliability of the sliding unit can be improved.

  FIG. 5 is a cross-sectional view of the low-pressure side end plate 19b as viewed from the high-pressure side compressor unit 20b side (Z-Z arrow view). The crankshaft 2 penetrates at the center of the high-pressure side end plate 9a, and the bolt 36 penetrates.

  As shown in FIGS. 5 and 1, the low pressure side end plate 19 b has a surface facing the low pressure side cylinder 10 a, and is a portion of the facing surface where the low pressure side vane 18 a moves, and the low pressure side cylinder A substantially arc-shaped low-pressure side end plate recess 44c is provided in the planar direction that communicates the end of the vane storage portion 41a with the space in the sealed container 13.

  The oil groove 44b provided in the partition plate 15 is a portion where the low-pressure side vane 18a moves, and the end of the low-pressure side cylinder vane storage portion 41a also communicates with the space in the sealed container 13.

  The low pressure side vane 18a is driven in the radial direction by the low pressure side roller 11a rotated by the low pressure side eccentric portion 5a, and the low pressure side vane, the low pressure side end plate side surface 18e and the low pressure side vane are driven by the oil groove 44b and the low pressure side end plate recess 44c. Since the partition plate side surface 18f can be opened to the refrigerating machine oil 47 interposed in the sealed container, it is possible to supply oil to the low-pressure side compressor section 20a and to improve the sliding section reliability.

  The high-pressure end plate recess 44a of the high-pressure end plate 9a, the oil groove 44b of the partition plate 15, and the recess 44c of the low-pressure end plate 19b all have an arcuate planar shape. However, the present invention is not limited to this planar shape, and any other planar shape can be used as long as it can form a space that can guide the refrigerating machine oil in the sealed container 13 to the vane storage portion provided in each cylinder.

  For example, the oil groove 44b provided in the partition plate 15 may have a substantially trapezoidal planar shape as shown in FIG. 6, or a substantially rectangular planar shape as shown in FIG. 6 and 7 show an example of the planar shape of the oil groove 44b of the partition plate 15. Similarly, the oil groove 44b is provided in the high pressure side end plate recess 44a and the low pressure side end plate 19b provided in the high pressure side end plate 9a. The planar shape of the low-pressure end plate recess 44c thus formed may be as shown in FIGS. In addition, a part of the planar shape of the recesses 44a, 44c and the oil groove 44b may be arcuate, trapezoidal, or rectangular, and at least the refrigerating machine oil in the sealed container 13 can be introduced into the vane storage part. Any other shape may be used.

  By providing a communication space, for example, an oil groove, in which the refrigerating machine oil in the hermetic container 13 communicates with the vane in the sliding portion with the vane of the high pressure side end plate, the low pressure side end plate, and the partition plate as described above, The compressor section 20b can be easily lubricated even with a low differential pressure lubrication structure unique to a two-stage rotary compressor, and the low-pressure side compressor section 20a is a highly diluted state of refrigeration oil during liquid refrigerant compression unique to a two-stage rotary compressor However, there is an advantage of ensuring the reliability of the vane sliding portion.

  In addition, when the communication path of the present embodiment is provided in each of the vane storage portions 41b and 41a of the high-pressure compressor section 20b and the low-pressure compressor section 20a, the communication path is provided in one of the upper and lower plate members. In this case, the refrigerating machine oil is introduced. However, the refrigerating machine oil can be introduced more efficiently by providing communication paths both above and below the vane storage portion.

  Moreover, although the present Example demonstrated with the structure provided with two compressor parts for high pressure and low pressure, it is good also as a structure provided with three compressor parts. In that case, a compressor section for intermediate pressure may be provided, and a communication space may be provided in two partition plates that close the axial direction of the compressor section.

1 is a longitudinal sectional view of a hermetic two-stage rotary compressor according to an embodiment of the present invention. FIG. 2 is a schematic diagram illustrating the relationship between a low-pressure compressor section and a high-pressure compressor section in the compressor section of FIG. It is XX arrow sectional drawing of FIG. It is a YY arrow sectional drawing of FIG. It is a ZZ arrow sectional drawing of FIG. It is a cross-sectional view of the partition plate in other embodiment of this invention. It is a cross-sectional view of the partition plate in other embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rotary compressor 2 Crankshaft 2a Center of rotation 5a Low pressure side eccentric part 5b High pressure side eccentric part 9 Main bearing 9a High pressure side end plate 10a Low pressure side cylinder 10b High pressure side cylinder 11a Low pressure side roller 11b High pressure side roller 13 Sealed container 14 Electric motor 15 Partition plate 18a Low pressure side vane 18b High pressure side vane 19 Intermediate container 19a Sub bearing 19b Low pressure side end plate 19c Outer wall portion 20a Low pressure side compressor portion 20b High pressure side compressor portion 23a Low pressure side compression chamber 23b High pressure side compression chamber 25a Suction port 25b Suction passages 26a, 26b Discharge port 26c Discharge port 28a, 28b Discharge valve 30 Intermediate flow path connection pipe 33 Intermediate discharge space 35 Cover 36 Bolt 41a Low pressure side cylinder vane storage part 41b High pressure side cylinder vane storage part 42, 43 Discharge port 44a High pressure Side end plate recess 44b Partition plate oil groove 44c Low pressure The end plate recess 47 refrigerating machine oil 48a low-pressure side spring 48b pressure side coil spring

Claims (5)

An electric motor, a crankshaft driven by the electric motor and having a plurality of eccentric parts, a plurality of compressor parts driven by the eccentric parts, and the plurality of compressor parts are closed in the direction of the crankshaft. A plurality of closing members;
The compressor portion includes a cylinder, a roller disposed in the cylinder and driven to rotate by the eccentric portion, two closing members that close the cylinder in the axial direction, and an outer periphery of the roller. A compression chamber having a vane that goes into and out of a storage portion provided in the cylinder according to the eccentric motion of the roller,
A hermetic rotary compressor having a communication space provided in at least one of two closing members that closes the compressor portion and communicating with the space in the hermetic container at a portion facing the storage portion of the vane.   2. The hermetic rotary compressor according to claim 1, wherein the closing member has a hole portion through which the crankshaft passes and a bearing portion continuous with the hole portion.   The hermetic rotary compressor according to claim 1, wherein the communication space provided in the closing member is a recess facing the vane.   4. The hermetic rotary compressor according to claim 1, wherein the planar shape of the communication space has a planar structure of any one of an arc shape, a trapezoidal shape, and a rectangular shape. Rotary compressor. An electric motor, a crankshaft driven by the electric motor and having a plurality of eccentric parts, a plurality of compressor parts driven by the eccentric parts, and the plurality of compressor parts are closed in the direction of the crankshaft. A plurality of closing members;
The compressor portion includes a cylinder, a roller disposed in the cylinder and driven to rotate by the eccentric portion, two closing members that close the cylinder in the axial direction, and an outer periphery of the roller. A compression chamber having a vane that goes into and out of a storage portion provided in the cylinder according to the eccentric motion of the roller,
A discharge pipe that is provided in the sealed container and discharges the working fluid to the outside;
Among the compressor sections, the compressor section that pressurizes the working fluid pressurized by another compressor section and discharges it from the discharge pipe is a discharge port that discharges the pressurized working fluid into the sealed container Have
A hermetic rotary compressor provided with a communication space provided in at least one of the closing members and facing a space in the hermetic container in a portion facing the vane housing.

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