JP4380734B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor, and more particularly to a rotary compressor used in, for example, an air conditioner or a refrigerator.

Examples of conventional rotary compressors include those described in JP-A-9-151888 (Patent Document 1). In Patent Document 1, a cylinder, end plate members (upper and lower bearing members) that form cylinder chambers (compression chambers) by closing both upper and lower end surfaces of the cylinder, and electric elements pivotally supported by these end plate members are disclosed. A rotary piston that rotates eccentrically by rotating the crankshaft, and discharges the refrigerant gas sucked and compressed by the eccentric rotation of the piston roller to the high-pressure side through the discharge port. Are listed. Here, the end plate member and the muffler cover (cover plate) form a muffler chamber communicating with the cylinder chamber.
JP-A-9-151888

  In the rotary compressor described in Patent Document 1, when the high-temperature and high-pressure refrigerant gas discharged from the cylinder chamber passes through the muffler chamber formed by the end plate member and the muffler cover, the low-temperature and low-pressure suction chamber in the cylinder chamber It will pass through the space that overlaps. As a result, the low-temperature and low-pressure intake gas is heated, and the volumetric efficiency is lowered.

  Here, a stagnation space in which the high-temperature and high-pressure discharge gas does not easily enter is provided in the muffler chamber, and the stagnation space is formed in a region overlapping the suction chamber in the cylinder chamber, so that the low-temperature and low-pressure suction gas is heated. It is possible to suppress the decrease in volumetric efficiency. However, for example, when the barrier for providing the stagnation space is formed integrally with the end plate member, the end plate member becomes complicated, and the manufacturability may decrease and the cost may increase.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a rotary compressor capable of improving volumetric efficiency while suppressing an increase in cost.

A rotary compressor according to the present invention is provided with an outer shell, a cylinder provided in the outer shell, having an open end, and attached to the open end of the cylinder, forming a cylinder chamber together with the cylinder, and supplying refrigerant gas from the cylinder chamber. An end plate member having a discharge port for discharging, a muffler cover that is attached to the opposite side of the cylinder with respect to the end plate member, and that forms a muffler chamber together with the end plate member via the discharge port; The blade is supported by the cylinder so as to protrude into the cylinder, and is provided in the cylinder chamber, and together with the blade, divides the cylinder chamber into a refrigerant gas suction chamber and a refrigerant gas discharge chamber and revolves around the central axis of the cylinder chamber The barrier portion provided in the muffler chamber forms a stagnation space separated from other parts in the muffler chamber on the end plate member. Is, stagnation space, holes than the plane passing through the central axis and the center of the cylinder chamber in a state where the most prominent in the cylinder chamber blade, which is located in the suction chamber side, for discharging the refrigerant gas from the muffler chamber, the plane The barrier portion is formed by covering the end plate member with the partition member, and the muffler chamber is formed so as to surround the central axis over the entire circumference.

  In the above configuration, since the stagnation space formed by the barrier portion is provided in the muffler chamber, the high-temperature and high-pressure gas discharged from the cylinder chamber to the muffler chamber is obstructed by the barrier portion and enters the stagnation space. It becomes difficult to do. Here, since the stagnation space is formed so as to overlap with the suction chamber side, a region where the low-temperature and low-pressure refrigerant gas sucked into the cylinder chamber and the high-temperature and high-pressure gas discharged into the muffler chamber overlap each other. It becomes difficult to pass and heat exchange between both is suppressed. Therefore, heating of the refrigerant gas sucked into the cylinder chamber is suppressed, and a decrease in volumetric efficiency is suppressed. On the other hand, as described above, when the barrier portion is formed in the muffler chamber, it is necessary to suppress an increase in cost due to a decrease in manufacturability of parts. In the rotary compressor according to the above configuration, a stagnation space can be formed without reducing the productivity of the end plate member and the muffler cover by forming the barrier portion by covering the end plate member with the partition member. . As described above, according to the rotary compressor of the present invention, it is possible to improve volumetric efficiency while suppressing an increase in cost.

  The “barrier part” does not need to be partitioned so as to completely block the stagnation space and the other part of the muffler chamber. In one typical example, the stagnation space and the other part of the muffler chamber are partitioned so as to be slightly communicated with each other.

  Further, the above-mentioned “stagnation space” does not necessarily have to be located on the suction chamber side from the above-described “plane passing through the center of the blade that protrudes most into the cylinder chamber and the central axis of the cylinder chamber”. If it has a portion located closer to the suction chamber than the plane, it corresponds to the “position toward the suction chamber” described above.

  In the rotary compressor according to one embodiment, the partition member includes a plate-like member having a bulge, and the bulge of the plate-like member is formed by pressing.

  In the rotary compressor according to one embodiment, the partition member is integrally formed by casting or sintering.

  According to the rotary compressor according to these embodiments, since the partition member can be easily manufactured, the volumetric efficiency can be improved while suppressing an increase in cost.

  In the rotary compressor according to one embodiment, the stagnation space is formed in a part in the height direction of the muffler chamber.

  According to the rotary compressor according to this embodiment, it is possible to prevent the refrigerant gas from flowing in the muffler chamber and causing overcompression. In the rotary compressor according to the present invention, the partition member is provided separately from the end plate member and the muffler cover to form the stagnation space. Therefore, the stagnation space is formed in a part of the height direction of the muffler chamber. Is easy.

  ADVANTAGE OF THE INVENTION According to this invention, in a rotary compressor, volume efficiency can be improved, suppressing the increase in cost.

  Embodiments of the present invention will be described below. Note that the same or corresponding parts are denoted by the same reference numerals, and the description thereof may not be repeated.

  Note that in the embodiments described below, when referring to the number, amount, and the like, the scope of the present invention is not necessarily limited to the number, amount, and the like unless otherwise specified. In the following embodiments, each component is not necessarily essential for the present invention unless otherwise specified. In addition, when there are a plurality of embodiments below, it is planned from the beginning to appropriately combine the configurations of the embodiments unless otherwise specified.

  FIG. 1 is a longitudinal sectional view showing a rotary compressor according to one embodiment of the present invention. Referring to FIG. 1, a rotary compressor according to the present embodiment includes a sealed container 10, a cylinder 20, end plate members 30, 40, 50, muffler covers 60, 70, eccentric pins 90, and rollers. 100.

  The cylinder 20, the end plate members 30, 40, 50, the muffler covers 60, 70, the eccentric pin 90, and the roller 100 are provided in the sealed container 10 and constitute a compression element. A motor 1 is provided above the compression element in the sealed container 10.

  The motor 1 includes a shaft 1A, a rotor 1B, and a stator 1C. Rotor 1B has, for example, a rotor body made of laminated electromagnetic steel plates and a magnet embedded in the rotor body. Stator 1C has, for example, a stator body made of laminated electromagnetic steel sheets and a coil wound around the stator body. The motor 1 generates an electromagnetic force by passing an electric current through the coil, and rotates the rotor 1B together with the shaft 1A by the electromagnetic force to drive the compression element via the shaft 1A.

  A suction pipe 3 for sucking refrigerant gas is connected to the sealed container 10, and an accumulator 2 is connected to the suction pipe 3. That is, the refrigerant gas is sucked into the sealed container 10 from the accumulator 2 through the suction pipe 3. The refrigerant gas introduced into the hermetic container 10 is obtained by controlling a condenser, an expansion mechanism, and an evaporator (none of which are shown) constituting the refrigeration system together with the rotary compressor shown in FIG. .

  The rotary compressor shown in FIG. 1 is configured to fill the inside of the hermetic container 10 with high-temperature and high-pressure discharge gas compressed in the cylinder 20. The gas is discharged from the discharge pipe 4 to the outside. In addition, lubricating oil 5 is stored at the bottom of the sealed container 10.

  On the lower side of the motor 1 in the sealed container 10, an end plate member 30 (upper end plate member), a cylinder 21 (upper cylinder), an end plate member 50 (intermediate end plate member), a cylinder 22 (lower cylinder) and an end are provided. The plate members 40 (lower end plate members) are arranged so as to be arranged in the above order from top to bottom along the rotation axis of the shaft 1A.

  The end plate members 30 and 50 are respectively attached to the upper and lower open ends of the upper cylinder 21. Further, the end plate members 50 and 70 are respectively attached to upper and lower opening ends of the lower cylinder 22.

  An upper cylinder chamber 21 </ b> A is formed by the upper cylinder 21 and the end plate members 30 and 50. The lower cylinder chamber 22A is formed by the lower cylinder 21 and the end plate members 50 and 70.

  The upper end plate member 30 includes a disk-shaped main body 31 and a boss 32 provided so as to protrude upward from the center of the main body 31. The main body 31 is provided with a discharge port (not shown) communicating with the cylinder chamber 21A.

  A discharge valve (not shown) is provided so as to be located on the opposite side of the cylinder 21 with respect to the main body 31. The discharge valve opens and closes a discharge port provided in the end plate member 30. Further, a cup-shaped muffler cover 60 (first muffler cover) is attached to the main body 31 so as to cover the discharge valve. The muffler cover 60 is fixed to the main body 31 by a fixing member such as a bolt.

  The muffler cover 60 and the end plate member 30 form a muffler chamber 60A (first muffler chamber). The muffler chamber 60A and the cylinder chamber 21A communicate with each other through the above-described discharge port.

  The lower end plate member 40 includes a disk-shaped main body portion 41 and a boss portion 42 provided so as to protrude downward from the central portion of the main body portion 41. The main body 41 is provided with a discharge port (not shown in FIG. 1) communicating with the cylinder chamber 22A.

  A discharge valve (not shown in FIG. 1) is provided so as to be located on the opposite side of the cylinder 22 with respect to the main body portion 41. This discharge valve opens and closes a discharge port provided in the end plate member 40. Further, a flat muffler cover 70 (second muffler cover) is attached to the main body 41 so as to cover the discharge valve. The muffler cover 70 is fixed to the main body 41 by a fixing member such as a bolt.

  The muffler cover 70 and the end plate member 40 form a muffler chamber 70A (second muffler chamber). The muffler chamber 70 </ b> A and the cylinder chamber 22 </ b> A are communicated with each other through a discharge port provided in the end plate member 40.

  A partition member 71 is provided between the muffler cover 70 and the end plate member 40. The partition member 71 and the end plate member 40 form a stagnation space 71A in which the refrigerant gas hardly enters the muffler chamber 70A.

  The muffler chamber 70 </ b> A and the muffler chamber 60 </ b> A are communicated with each other through holes (not shown) formed in the end plate member 40, the cylinder 22, the end plate member 50, the cylinder 21, and the end plate member 30. The muffler chamber 60 </ b> A and the space outside the muffler cover 60 are communicated with each other through a hole (not shown) formed in the muffler cover 60.

  The cylinder 20, the end plate members 30, 40, 50, the muffler covers 60, 70, and the partition member 71 are integrally fixed by a fixing member such as a bolt. Further, the end plate member 30 is fixed to the sealed container 10 by welding or the like. Thereby, the compression element of the rotary compressor is fixed to the hermetic container 10.

  One end of the shaft 1 </ b> A is supported by end plate members 30 and 40. That is, the shaft 1A is cantilevered. One end portion (support end side) of the shaft 1A enters the cylinder chambers 21A and 22A.

  Upper and lower eccentric pins 90 (91, 92) are attached to the shaft 1A. The upper eccentric pin 91 is provided so as to be located in the cylinder chamber 21A. Further, the lower eccentric pin 92 is provided so as to be located in the cylinder chamber 22A. The rollers 100 (101, 102) are fitted into the upper and lower eccentric pins 90, respectively. Therefore, the upper roller 101 revolves in the cylinder chamber 21A, and the lower roller 102 revolves in the cylinder chamber 22A. By the revolving motion of the rollers 101 and 102, the refrigerant gas is compressed in the cylinder chambers 21A and 22A. The upper and lower eccentric pins 91 and 92 are formed so that their phases are shifted by 180 ° with respect to the rotation axis of the shaft 1A.

Next, the compression action in the cylinder 22 will be described with reference to FIG.
As shown in FIG. 2, the cylinder chamber 22A is partitioned into a suction chamber 212A (low pressure chamber) and a discharge chamber 212B (high pressure chamber) by a roller 102 and a blade 112 provided integrally with the roller 102. The suction pipe 3 communicates with the suction chamber 212A, and the discharge port communicates with the discharge chamber 212B. Two semi-cylindrical bushes 112A are in close contact with both surfaces of the blade 112. The bush 112 </ b> A is held by the cylinder 22. Thereby, the cylinder chamber 22A is sealed. Note that lubrication with the lubricating oil 5 is performed between the blade 112 and the bush 112 </ b> A and between the bush 112 </ b> A and the cylinder 22.

  Since the eccentric pin 92 is eccentric with respect to the central axis 1A0 of the shaft 1A, the eccentric pin 92 rotates eccentrically with the rotation of the shaft 1A. As a result, the roller 102 revolves while contacting the inner surface of the cylinder chamber 22A. As the roller 102 revolves in the cylinder chamber 22A, the blade 112 moves forward and backward while being sandwiched between the two bushes 112A. As a result, the low-pressure refrigerant gas is sucked into the suction chamber 212A from the suction pipe 3, the gas is compressed in the discharge chamber 212B, and the high-pressure refrigerant gas is discharged from the discharge port. The refrigerant gas discharged from the discharge port is discharged to the outside of the muffler cover 60 after passing through the muffler chambers 70A and 60A.

  FIG. 2 shows a state in which the blade 112 protrudes most into the cylinder chamber 22A. In this state, the suction chamber 212A is located on the left side (suction pipe side) in FIG. 2 with respect to the plane S2 passing through the center of the blade 112 and the central axis 1A0 of the shaft 1A, and the discharge chamber 212B is on the plane S2. On the other hand, it is located on the right side (discharge port side) in FIG.

  The refrigerant gas sucked into the suction chamber 212A from the suction pipe 3 is in a low temperature and low pressure state. On the other hand, the refrigerant gas discharged from the discharge port to the muffler chamber 70A is in a high temperature and high pressure state. Heat exchange is performed between the low-temperature and low-pressure refrigerant gas and the high-temperature and high-pressure refrigerant gas through the end plate member 40 that partitions the cylinder chamber 22A and the muffler chamber 70A. With this heat exchange, there is a concern that the refrigerant gas sucked into the cylinder chamber 22A is heated and the volumetric efficiency is lowered.

  3-5 is a figure which shows the end plate member 40, the partition member 71, and the muffler cover 70, respectively. In FIG. 4, for convenience of illustration and description, a portion corresponding to the stagnation space 71 </ b> A is hatched.

  As shown in FIG. 3, the end plate member 40 has a discharge hole 40A communicating with the cylinder chamber 22A, a communication hole 40B communicating with the muffler chamber 70A, and a bolt hole 40C through which a bolt is inserted. Further, a discharge valve 132 for opening and closing the discharge port 40A is attached to the end plate member 40. The refrigerant gas in the muffler chamber 70A flows into the muffler chamber 60A through the communication hole 40B.

  As shown in FIG. 4, the partition member 71 is a member formed by pressing a flat plate-like member, and is provided at a position where the bulge for forming the stagnation space 71A and the discharge valve 132 are attached. The formed opening 71B, a communication hole 71C communicating with the communication hole 40B, and a bolt hole 71D communicating with the bolt hole 40C.

  As shown in FIG. 5, the muffler cover 70 is a member formed by pressing a flat plate-like member, and a bulge for forming the muffler chamber 70A and bolts communicating with the bolt holes 40C and 71D. Hole 70B.

  The partition member 71 and the muffler cover 70 are fixed to the end plate member 40 by inserting the bolts into the bolt holes 40C, 71D, and 70B shown in FIGS. As a result, a muffler chamber 70A into which high-temperature and high-pressure refrigerant gas flows from the discharge port 40A and a stagnation space 71A in the muffler chamber 70A where high-temperature and high-pressure gas hardly flows are formed.

  As shown in FIG. 5, the muffler chamber 70A is formed so as to surround the central axis 1A0 of the shaft 1A over the entire circumference. Moreover, as shown in FIG. 1, the stagnation space 71A is formed in a part of the height direction (vertical direction in FIG. 1) of the muffler chamber 70A. By forming the stagnation space 71A in a part in the height direction of the muffler chamber 70A, it is possible to suppress the deterioration of the flow of the refrigerant gas in the muffler chamber 70A and to reduce overcompression.

  The stagnation space 71A is a sealed or opened space. In other words, the stagnation space 71A is open, that is, a passage that connects the stagnation space 71A and another space in the sealed container 10 is formed. By opening the stagnation space 71A, it is possible to prevent air from remaining in the sealed container 10 during evacuation.

  The stagnation space 71A is provided on the suction pipe 3 side with respect to the plane S2. That is, the stagnation space 71A is located in a portion overlapping the suction chamber 212A (see FIG. 2) in the cylinder chamber 22A. By forming such a stagnation space 71A, it becomes difficult for the high-temperature and high-pressure refrigerant gas discharged into the muffler chamber 70A to pass through the portion of the cylinder chamber 22A that overlaps the suction chamber 212A, and the high-temperature and high-pressure in the muffler chamber 70A. Heat exchange between the gas and the low-temperature and low-pressure gas just taken into the cylinder chamber 22A is suppressed. As a result, a decrease in volumetric efficiency is suppressed.

  As described above, by forming the stagnation space 71A in the muffler chamber 70A, heating of the refrigerant gas sucked into the cylinder chamber 22A is suppressed, and a decrease in volumetric efficiency is suppressed. On the other hand, when the stagnation space 71A is formed, for example, if a barrier portion for defining the stagnation space 71A is provided integrally with the end plate member 40 and the muffler cover 70, the shape of the parts becomes complicated and the manufacturing cost is reduced. There is concern about the increase.

  In the present embodiment, the stagnation space 71A is formed by covering the end plate member 40 with a partition member 71 having a bulge. By doing so, the stagnation space 71A can be formed in the muffler chamber 70A without performing complicated processing on the end plate member 40 and the muffler cover 70. The partition member 71 can be formed by pressing a plate-like member. Therefore, according to the rotary compressor according to the present embodiment, it is possible to form the stagnation space 71A in the muffler chamber 70A while suppressing an increase in manufacturing cost.

  6 is a view showing a modified example of the partition member 71, and FIG. 7 is a longitudinal sectional view showing a state in which the partition member 71 shown in FIG. 6 and 7, the partition member 71 according to this modification is integrally formed by sintering or casting. Even with such a partition member 71, it is possible to form the stagnation space 71 </ b> A in the muffler chamber 70 </ b> A while suppressing an increase in manufacturing cost, similarly to the partition member 71 shown in FIG. 4.

  The above contents are summarized as follows. That is, the rotary compressor according to the present embodiment includes a sealed container 10 as an “outer shell body”, a cylinder 22 provided in the sealed container 10, a cylinder 22, and a cylinder chamber 22 A together with the cylinder 22. An end plate member 40 having a discharge port 40A for discharging and discharging refrigerant gas from the cylinder chamber 22A is attached to the opposite side of the cylinder 22 with respect to the end plate member 40, and communicates with the cylinder chamber 22A via the discharge port 40A. The muffler cover 70 that forms the muffler chamber 70A together with the end plate member 40, the blade 112 supported by the cylinder 22 so as to protrude into the cylinder chamber 22A, and the cylinder chamber 22A together with the blade 112 provided in the cylinder chamber 22A. Is divided into a refrigerant gas suction chamber 212A and a refrigerant gas discharge chamber 212B, and the cylinder chamber 2 And a roller 102 which revolves around the central axis of the A (central axis 1A0 of the shaft 1A). The partition member 71 as a “barrier portion” provided in the muffler chamber 70 </ b> A forms a stagnation space 71 </ b> A that is partitioned from other portions in the muffler chamber 70 </ b> A on the end plate member 40. That is, the “barrier portion” is formed by covering the partition member 71 on the end plate member 40. The stagnation space 71A is located closer to the suction chamber 212A than the plane S2 that passes through the center of the blade 112 and the central axis 1A0 that protrudes most into the cylinder chamber 22A.

  In the above example, the example in the lower muffler chamber 70A has been described. However, the idea of the present invention can naturally be applied to the upper muffler chamber 60A, and a rotary compressor having one cylinder is used. Of course, it is also applicable.

  In the above example, the rotary compressor in which the blade and the roller are integrated has been described. However, the idea of the present invention is naturally applicable to a rotary compressor in which the blade and the roller are formed separately. Is possible.

  Although the embodiments of the present invention have been described above, the embodiments disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a longitudinal section showing a rotary compressor concerning one embodiment of the present invention. It is a figure for demonstrating the compression effect | action in the cylinder chamber in the rotary compressor shown by FIG. It is a figure which shows the end plate member in the rotary compressor shown by FIG. It is a figure which shows the partition member for stagnation space formation in the rotary compressor shown by FIG. It is a figure which shows the muffler cover in the rotary compressor shown by FIG. It is a figure which shows the modification of the partition member for stagnation space formation. It is a longitudinal cross-sectional view which shows the state which attached the partition member shown by FIG. 6 to the end plate member.

Explanation of symbols

  1 motor, 1A shaft, 1A0 central axis, 1B rotor, 1C stator, 2 accumulator, 3 suction pipe, 4 discharge pipe, 10 sealed container, 20, 21, 22 cylinder, 21A, 22A cylinder chamber, 30, 40, 50 end Plate member, 40A discharge port, 40B communication hole, 40C bolt hole, 31, 41 body portion, 32, 42 boss portion, 60, 70 muffler cover, 60A, 70A muffler chamber, 70B bolt hole, 71 partition member, 71A stagnation space , 71B opening, 71C communication hole, 71D bolt hole, 90, 91, 92 eccentric pin, 100, 101, 102 roller, 112 blade, 112A bush, 132 discharge valve, 212A suction chamber, 212B discharge chamber.

Claims (4)

An outer shell (10), a cylinder (22) provided in the outer shell (10) and having an open end;
An end plate attached to the open end of the cylinder (22), forming a cylinder chamber (22A) together with the cylinder (22), and having a discharge port (40A) for discharging the refrigerant gas from the cylinder chamber (22A) A member (40);
A muffler chamber (70A) attached to the opposite side of the cylinder (22) with respect to the end plate member (40) and communicating with the cylinder chamber (22A) via the discharge port (40A) is defined as the end plate member. A muffler cover (70) formed with (40);
A blade (112) supported by the cylinder (22) so as to protrude into the cylinder chamber (22A);
The cylinder chamber (22A) is provided in the cylinder chamber (22A) and partitions the cylinder chamber (22A) into the refrigerant gas suction chamber (212A) and the refrigerant gas discharge chamber (212B) together with the blade (112). A roller (102) revolving around the central axis (1A0) of the chamber (22A),
By the barrier portion (71) provided in the muffler chamber (70A), a stagnation space (71A) partitioned from other portions in the muffler chamber (70A) is formed on the end plate member (40),
The stagnation space (71A) is more than a plane (S2) passing through the center of the blade (112) in the state of most protrusion in the cylinder chamber (22A) and the central axis (1A0) of the cylinder chamber (22A). The holes (40B, 71C) for discharging the refrigerant gas from the muffler chamber (70A) are located closer to the discharge chamber (212B) than the plane (S2). ,
The barrier portion (71) is formed by covering a partition member (71) on the end plate member (40),
The muffler chamber (70A) is a rotary compressor formed so as to surround the entire circumference of the central axis (1A0). The partition member (71) includes a plate-like member having a bulge,
The rotary compressor according to claim 1, wherein the swelling of the plate-like member is formed by pressing.   The rotary compressor according to claim 1, wherein the partition member (71) is integrally formed by casting or sintering.   The rotary compressor according to any one of claims 1 to 3, wherein the stagnation space (71A) is formed in a part of the muffler chamber (70A) in a height direction.

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