JP5560807B2 - Compressor - Google Patents

Description

  The present invention relates to a multi-cylinder rotary compressor applied as a compressor for an air conditioner, a refrigerator, a refrigerator, or a hot water heater.

  A conventional multi-cylinder rotary compressor has a configuration in which each suction pipe piped from an accumulator is attached to each suction hole communicating with a plurality of cylinder chambers housed in a cylindrical casing. However, such a configuration has a problem that the pressure resistance of the cylindrical casing is insufficient in the vicinity of each suction hole. Accordingly, a cylindrical casing provided with a reinforcing plate having an area including each suction hole has been proposed (see Patent Document 1).

Japanese Utility Model Publication No. 5-24988

  However, the conventional cylindrical casing as described above has a problem that the manufacturing cost increases because a reinforcing plate is required. In addition to the measures described above, in order to improve the pressure strength of each suction hole portion, it is conceivable to reduce the diameter of each suction hole to increase the distance between the suction holes. Such a countermeasure has a problem that the performance of the compressor deteriorates due to an increase in suction pressure loss.

  The object of the present invention is to solve the above-mentioned problems, and can reduce the manufacturing cost without providing a reinforcing plate as in the prior art, and reduce the performance of the compressor by increasing the suction pressure loss. It is an object to provide a compressor capable of improving the pressure resistance between suction holes having a low strength in the casing without causing them.

  A compressor according to a first aspect of the present invention includes a plurality of cylinders each having a cylinder chamber, and a plurality of suction holes that accommodate the plurality of cylinders and that correspond to the plurality of cylinders and that are arranged along the axial direction thereof. And at least one of the plurality of suction holes has a length along the axial direction of the casing shorter than a length along the circumferential direction.

  In this compressor, in order to improve the pressure resistance strength between the conventional suction holes, the diameter of the suction holes is reduced and the distance between the suction holes is made longer than before. However, in the present invention, at least one suction hole has an elliptical shape so that the distance between the suction hole and the suction hole adjacent to the suction hole is larger than the conventional one. Therefore, the opening area of the suction hole can be increased as compared with the countermeasure for reducing the diameter of the suction hole. Therefore, it is possible to suppress the performance degradation of the compressor while making the distance between the suction holes longer than before. Further, in the present invention, since it is not necessary to provide a conventional reinforcing plate in order to improve the pressure resistance between the suction holes, the manufacturing cost of the compressor can be reduced as compared with the conventional case.

  In addition, the “suction hole” in the present invention indicates that the suction pipe is connected from the outside of the casing. Further, the suction pipe may be directly connected to the “suction hole”, or the suction pipe may be connected via another member (for example, an inlet tube or a joint pipe).

  The compressor according to the second invention is the compressor according to the first invention, wherein the opening area of at least one suction hole is a circular suction hole whose diameter is the length along the axial direction of the casing in the suction hole. Larger than the opening area.

  In this compressor, the opening area can be made larger than that of the circular suction hole by making the at least one suction hole elliptical.

  As described above, according to the present invention, the following effects can be obtained.

  In the first invention, in order to improve the pressure resistance strength between the conventional suction holes, the diameter of the suction holes is reduced and the distance between the suction holes is made longer than in the conventional case. In the present invention, the distance between the suction hole adjacent to the suction hole is made conventional by making the at least one suction hole elliptical. Therefore, the opening area of the suction hole can be increased as compared with the countermeasure for reducing the diameter of the suction hole. Therefore, it is possible to suppress the performance degradation of the compressor while making the distance between the suction holes longer than before. Further, in the present invention, since it is not necessary to provide a conventional reinforcing plate in order to improve the pressure resistance between the suction holes, the manufacturing cost of the compressor can be reduced as compared with the conventional case.

  In the second invention, the opening area can be made larger than that of the circular suction hole by making the at least one suction hole elliptical.

It is a schematic block diagram of the rotary compressor which concerns on one Embodiment of this invention. It is an enlarged view of the part enclosed with the dashed-dotted line of the rotary compressor shown in FIG. It is a side view of a cylindrical casing. It is explanatory drawing which shows the modification of the suction hole formed in the cylindrical casing.

  Hereinafter, an embodiment of a compressor according to the present invention will be described based on the drawings. FIG. 1 is a schematic configuration diagram of a two-cylinder CO2 refrigerant rotary compressor according to an embodiment of the present invention. FIG. 2 is an enlarged view of a portion surrounded by a one-dot chain line of the rotary compressor 1 (compressor) shown in FIG. The rotary compressor 1 compresses the compressed refrigerant introduced from the accumulator 2 and discharges the compressed refrigerant from the discharge flow path 11 arranged at the upper end portion thereof.

<Overall configuration of rotary compressor>
As shown in FIG. 1, the rotary compressor 1 includes a cylindrical casing 10 (casing), and a drive mechanism 20 and a compression mechanism 30 disposed in the cylindrical casing 10. The rotary compressor 1 is a so-called high-pressure dome type compressor, and a compression mechanism 30 is disposed below the drive mechanism 20 in the cylindrical casing 10. In addition, the lubricating oil 40 supplied to each sliding portion of the compression mechanism 30 is stored in the lower portion of the cylindrical casing 10.

<Drive mechanism>
The drive mechanism 20 is provided to drive the compression mechanism 30 and includes a motor 21 serving as a drive source and a shaft 22 attached to the motor 21.

  The motor 21 includes a rotor 21a and a stator 21b disposed on the radially outer side of the rotor 21a via an air gap. A shaft 22 is rotatably attached to the rotor 21a. And the rotor 21a has the rotor main body which consists of a laminated | stacked electromagnetic steel plate, and the magnet embed | buried under this rotor main body. The stator 21b has a stator main body made of iron and a coil wound around the stator main body. The motor 21 rotates the rotor 21 a together with the shaft 22 by electromagnetic force generated in the stator 21 b by passing an electric current through the coil.

  The shaft 22 rotates with the rotor 21a described above to rotate the roller 34 and the roller 37 of the compression mechanism 30. The shaft 22 is provided with an eccentric portion 22a so as to be positioned in a cylinder chamber B1 of the front cylinder 33 described later, and is provided with an eccentric portion 22b so as to be positioned in a cylinder chamber B2 of the rear cylinder 36. . Rollers 34 and 37 are attached to these eccentric portions 22a and 22b, respectively. Accordingly, as the shaft 22 rotates, the roller 34 attached to the eccentric portion 22a rotates in the cylinder chamber B1, and the roller 37 attached to the eccentric portion 22b rotates in the cylinder chamber B2. The eccentric portion 22a and the eccentric portion 22b are disposed at positions shifted by 180 ° in the rotation direction of the shaft 22.

<Compression mechanism>
On the other hand, the compression mechanism 30 is provided to compress the refrigerant sucked from the accumulator 2 through the suction pipe 3 and the suction pipe 6. The refrigerant discharged by the compression mechanism 30 passes through the air gap between the stator 21b and the rotor 21a of the drive mechanism 20, cools the drive mechanism 20, and is then discharged from the discharge passage 11. The compression mechanism 30 includes a front muffler 31, a front head 32, a front cylinder 33, a middle plate 35, a rear cylinder 36, and a downward direction along the rotation axis of the shaft 22 of the drive mechanism 20. A rear head 38 and a rear muffler 39 are provided.

  The front muffler 31 silences the refrigerant discharged from a discharge port (not shown) provided in the front head 32 and discharges it to the primary space. The front muffler 31 is attached to the front head 32. The front head 32 is joined to the upper surface of the front cylinder 33 and closes the opening at the upper end of the cylinder chamber B1. The front head 32 is provided with a discharge port (not shown) for discharging the refrigerant compressed in the cylinder chamber B1 to the muffler space A1 formed by the front muffler 31 described above.

  The front cylinder 33 is provided with a cylinder chamber B1 at the center thereof. In the cylinder chamber B <b> 1, a roller 34 that moves eccentrically with the rotation of the shaft 22 is disposed. The cylinder chamber B1 communicates with the muffler space A1 through the above-described discharge port. Accordingly, the refrigerant compressed by the eccentric rotational movement of the roller 34 attached to the eccentric portion 22a of the shaft 22 is guided from the cylinder chamber B1 to the muffler space A1. The roller 34 performs eccentric rotational movement along the inner peripheral surface of the cylinder chamber B <b> 1, and compresses the refrigerant sucked from the accumulator 2. The end of a blade (not shown) is in contact with the outer peripheral surface of the roller 34, and each of the roller 34 and the blade is configured as a separate body.

  The middle plate 35 is disposed between the front cylinder 33 and the rear cylinder 36. The middle plate 35 closes the opening below the cylinder chamber B1 of the front cylinder 33, and closes the opening above the cylinder chamber B2 of the rear cylinder 36. The rear cylinder 36, the roller 37, the rear head 38, and the rear muffler 39 are the same as the front cylinder 33, the roller 34, the front head 32, and the front muffler 31 from the viewpoint of each function, and thus the description thereof is omitted. The refrigerant compressed in the cylinder chamber B2 of the rear cylinder 36 passes through the muffler space A2 formed by the rear head 38 and the rear muffler 39, and then enters the rear head 38, the rear cylinder 36, the middle plate 35, and the front cylinder 33. The air is guided to the muffler space A1 through a communication hole (not shown) that communicates and a communication hole (not shown) formed in the front head 32.

  As shown in FIG. 2, the front cylinder 33 has a suction hole 33a communicating with the cylinder chamber B1. In an elliptical suction hole 10a formed in the cylindrical casing 10, a joint pipe 5 having the same outer peripheral surface as the suction hole 10a is fixed by brazing or the like. A rear end portion 4 a of the inlet tube 4 having the same elliptical outer peripheral surface as the inner peripheral surface of the joint tube 5 is fixed to the joint tube 5. The rear end portion 4a of the inlet tube 4 has an outer peripheral surface having the same elliptical shape as the inner peripheral surface of the rear end portion 4a, and is used for supplying refrigerant from the outside of the cylindrical casing 10 to the cylinder chamber B1. Pipe 3 is connected. Further, the distal end portion 4 b of the inlet tube 4 is inserted into the suction hole 33 a of the front cylinder 33 through the suction hole 10 a formed in the cylindrical casing 10.

  As shown in FIG. 2, the rear cylinder 36 has a suction hole 36a communicating with the cylinder chamber B2. A joint pipe 8 having an elliptical outer peripheral surface identical to the suction hole 10b is fixed to the elliptical suction hole 10b formed in the cylindrical casing 10 by brazing or the like. A rear end portion 7 a of the inlet tube 7 having the same elliptical outer peripheral surface as the inner peripheral surface of the joint tube 8 is fixed to the joint tube 8. The rear end portion 7a of the inlet tube 7 has an outer peripheral surface having the same elliptical shape as the inner peripheral surface of the rear end portion 7a, and is used for supplying refrigerant from the outside of the cylindrical casing 10 to the cylinder chamber B2. Pipe 6 is connected. Further, the distal end portion 7 b of the inlet tube 7 is inserted into the suction hole 36 a of the rear cylinder 36 through the suction hole 10 b formed in the cylindrical casing 10.

  FIG. 3 is a side view of the cylindrical casing. 3A to 3C show the periphery of the suction holes 10a and 10b arranged along the axial direction of the cylindrical casing 10 of the present invention, along the axial direction of the cylindrical casing 50 of the comparative example of the present invention. The periphery of the suction holes 51 and 52 arranged in this manner and the periphery of the suction holes 61 and 62 arranged along the axial direction of the cylindrical casing 60 of the conventional example are shown. The centers C1 to C6 in the figure indicate the centers of the suction holes 10a, 10b, 51, 52, 61, 62. A distance L6 in the figure indicates a distance between a one-dot chain line connecting the centers C1, C3, and C5 and a one-dot chain line connecting the centers C2, C4, and C6. That is, in the conventional example, the comparative example, and the present invention, the respective center distances are the same at L6.

  As shown in FIG. 3A, the suction holes 61 and 62 of the conventional example have the same shape, and are formed in a circular shape having a length L3 along the axial direction of the cylindrical casing 60 as a diameter. Yes. Further, the distance L5 in the figure indicates the distance between the suction holes 61 and 62 of the conventional example.

  As shown in FIG. 3B, the suction holes 51 and 52 of the comparative example have the same shape, and the diameter L1 is for the purpose of improving the pressure resistance between the suction holes 61 and 62 of the conventional example. The suction holes 61 and 62 of the conventional example are designed to be smaller than the diameter L3. Accordingly, the distance L4 between the suction holes 51 and 52 of the comparative example is longer than the distance L5 between the suction holes 61 and 62 of the conventional example. However, in the comparative example, since the opening areas of the suction holes 51 and 52 are smaller than the opening areas of the suction holes 61 and 62 of the conventional example, the suction pressure loss increases and the performance of the rotary compressor is deteriorated. is there.

  As shown in FIG. 3C, the distance between the suction holes 10a and 10b of the present invention is the same distance L4 as that between the suction holes 51 and 52 of the comparative example, and the distance between the suction holes 61 and 62 of the conventional example. It is longer than L5. Further, in the suction holes 10a and 10b of the present invention, the length L1 along the axial direction of the cylindrical casing 10 is equal to the diameter L1 of the suction holes 51 and 52 of the comparative example, and is shorter than the length L2 along the circumferential direction. And have the same elliptical shape. Thereby, in the cylindrical casing 10 of this invention, the opening area of the suction holes 10a and 10b is larger than the opening area of the suction holes 51 and 52 of a comparative example.

[Features of rotary compressor of this embodiment]
The rotary compressor 1 of the present embodiment has the following features.

  In the rotary compressor 1 of the present embodiment, the distance between the suction holes 10a and 10b is secured longer than the distance L5 between the suction holes 61 and 62 of the conventional example, and the pressure resistance strength between the suction holes 10a and 10b is higher than that of the conventional one. In addition, by making the suction holes 10a and 10b elliptical, the opening areas of the suction holes 10a and 10b can be made larger than the opening areas of the suction holes 51 and 52 of the comparative example. Therefore, in the cylindrical casing 10 of the present invention, an increase in the suction pressure loss can be suppressed and the performance deterioration of the rotary compressor 1 can be suppressed as compared with the cylindrical casing 50 of the comparative example.

  Moreover, in the rotary compressor 1 of this embodiment, since it is not necessary to provide the reinforcement board like the past in order to improve the pressure strength between each suction hole 10a, 10b, the manufacturing cost of the rotary compressor 1 compared with the past. Can be reduced.

  Further, in the rotary compressor 1 of the present embodiment, the opening area can be made larger than that of the circular suction hole by making each suction hole 10a, 10b elliptical.

  As mentioned above, although embodiment of this invention was described based on drawing, it should be thought that a specific structure is not limited to these embodiment. The scope of the present invention is shown not only by the above description of the embodiments but also by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  In the above-described embodiment, the example in which the suction pipes 3 and 6 are connected to the suction holes 10a and 10b via the inlet tubes 4 and 7 and the joint pipes 5 and 8 has been described. However, the suction pipes 3 and 6 may be directly connected to the suction holes 10a and 10b.

  In the above-described embodiment, the example in which the suction holes 10a and 10b are all formed in an elliptical shape has been described. The present invention is not limited to such an embodiment. For example, as shown in FIG. 4, the distance between the centers C1 and C7 of the suction holes 10a and 110b is set to L6 (see FIG. 3) which is the same as the distance between the centers C5 and C6 of the suction holes 61 and 62 of the conventional example. In the maintained state, the cylindrical casing 110 in which only the suction hole 10a is formed in an elliptical shape and the other suction hole 110b is formed in a conventional circular shape may be configured. According to such a configuration, the distance L7 between the suction holes 10a and 110b is secured longer than the distance L5 (see FIG. 3A) between the suction holes 61 and 62 of the conventional example, and between the suction holes 10a and 110b. By increasing the opening area of the suction hole 10a to be larger than the opening area of the suction hole 110b, the increase in suction pressure loss due to the elliptical shape of the suction hole 10a can be suppressed.

  In the above-described embodiment, the rotary compressor 1 having the cylindrical casing 10 in which the two suction holes 10a and 10b are formed has been described. The present invention is not limited to such an embodiment. For example, in a cylindrical casing having three or more suction holes, at least one suction hole may be formed in an elliptical shape.

  In the above-described embodiment, the compressor using the CO2 refrigerant has been described. However, the present invention is not limited to this, and can be applied to a compressor using a refrigerant other than the CO2 refrigerant.

  In the above-described embodiment, the example in which the present invention is applied to a two-cylinder rotary compressor has been described. However, the present invention is not limited to this, and a one-cylinder rotary compressor also includes a three-cylinder or more rotary compressor. The present invention can be applied to a compressor, and the present invention can also be applied to a scroll compressor other than a rotary compressor.

  In the above-described embodiment, the example in which the roller 34 and the blade are configured separately from each other has been described. However, the present invention is not limited to such an embodiment. The roller 34 and the blade may be integrated.

  If the present invention is used, the manufacturing cost can be reduced without providing a reinforcing plate as in the prior art, and the pressure resistance between the suction holes, which are weak in the casing, without reducing the performance of the compressor due to the increase in suction pressure loss. A compressor capable of improving the efficiency can be obtained.

1 Rotary compressor (compressor)
3, 6 Suction piping 4, 7 Inlet tube 10, 110 Cylindrical casing (casing)
10a, 10b, 110b Suction hole 33 Front cylinder 36 Rear cylinder B1, B2 Cylinder chamber

Claims (2)

A plurality of cylinders each having a cylinder chamber;
A casing that houses the plurality of cylinders and has a plurality of suction holes respectively corresponding to the plurality of cylinders and arranged along the axial direction thereof;
At least one of the plurality of suction holes is characterized in that the length along the axial direction of the casing is shorter than the length along the circumferential direction. 2. The compression according to claim 1, wherein an opening area of the at least one suction hole is larger than an opening area of a circular suction hole whose diameter is a length along the axial direction of the casing in the suction hole. Machine.

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