WO2018189827A1

WO2018189827A1 - Enclosed compressor and refrigeration cycle device

Info

Publication number: WO2018189827A1
Application number: PCT/JP2017/014985
Authority: WO
Inventors: 祐一朗今川; 勝巳遠藤
Original assignee: 三菱電機株式会社
Priority date: 2017-04-12
Filing date: 2017-04-12
Publication date: 2018-10-18

Abstract

This enclosed compressor is provided with a cylindrical cylinder forming a compression chamber that compresses refrigerant through the rotation of a crankshaft, and a bearing that is disposed in an axial-direction end surface of the cylinder and rotatably supports the crankshaft. Formed in the bearing are a discharge port that discharges refrigerant compressed in the compression chamber, and a recessed counterbore hole that is provided to the periphery of the discharge port and that has the capacity needed for the refrigerant discharged from the discharge port to flow. The discharge port is provided so as to be eccentric relative to the counterbore hole toward the bearing center, and a discharge cutout through which the compression chamber and the discharge port communicate is provided to an inner-wall portion of the cylinder, which faces the eccentric discharge port.

Description

Hermetic compressor and refrigeration cycle apparatus

The present invention relates to a hermetic compressor and a refrigeration cycle apparatus.

A conventional hermetic compressor includes an electric motor unit including a stator and a rotor, and a compression mechanism unit that is coupled to the electric motor unit via a crankshaft and compresses the refrigerant by rotation of the crankshaft. It has the structure arrange | positioned inside the container. Then, the crankshaft is rotated by the electric motor section, and the compression mechanism section is driven by the rotation of the crankshaft, whereby the low-pressure refrigerant gas sucked from the suction pipe is compressed by the compression mechanism section to become high-pressure refrigerant gas, and is discharged from the discharge pipe. It is discharged out of the closed container.

The compression mechanism portion is provided in the cylinder, the rolling piston that fits the eccentric shaft portion of the crankshaft, the bearing that is installed on both end surfaces of the cylinder in the axial direction, and rotatably supports the crankshaft. A vane or the like slidably disposed in the vane groove is provided. The cylinder has a compression chamber formed therein by closing both end faces in the axial direction with end plate portions of the bearings.

In the above configuration, the rolling piston performs an eccentric motion in the cylinder, and as a result, the refrigerant sucked into the compression chamber is compressed with the rotation of the crankshaft.

Compressed high-pressure refrigerant gas is discharged into a sealed container from a discharge port provided in the recess of the bearing. The recess of the bearing is provided with a discharge valve device composed of a valve seat, valve, valve retainer and rivet so that when the compression chamber reaches a predetermined pressure, the valve is pushed up to open the discharge port (For example, refer to Patent Document 1). The discharge valve device is configured such that a valve and a valve presser are sequentially placed on a valve seat, and these are fastened to a bearing with a rivet.

Although details are not shown in Patent Document 1, the inner wall of the cylinder is provided with a discharge notch that is partially cut out in accordance with the outer shape of the discharge port, thereby reducing the flow resistance immediately before the refrigerant gas is discharged and reducing the pressure loss. It is common to reduce this. In addition, the recess provided in the bearing in Patent Document 1 includes a first counterbore hole concentric with the discharge port, a second counterbore hole (counterbore portion 13b) eccentric to the first counterbore hole, and a first counterbore hole. It is comprised from the linear part extended in one direction from a part of outer peripheral surface. The first counterbore hole and the second counterbore hole provided around the discharge port are provided to ensure a sufficient space for the refrigerant discharged from the discharge port to flow. These first counterbore holes and second counterbore holes suppress the flow resistance of the refrigerant immediately after discharge, thereby reducing pressure loss.

JP 2008-101503 A

In Patent Document 1, the pressure loss of the refrigerant before and after the discharge is reduced by the discharge notch and the counterbore hole. However, the discharge notch provided on the inner wall of the cylinder is an ineffective space that does not contribute to compression, and this ineffective space becomes dead volume, increasing recompression loss and heating loss, and reducing the efficiency of the hermetic compressor. Invite. For this reason, reduction of the discharge notch is required, but Patent Document 1 does not discuss this point at all.

Moreover, in patent document 1, sufficient space for the refrigerant | coolant immediately after discharge to flow by providing two of the 1 counterbore hole concentric with a discharge port, and the 2nd counterbore hole eccentric with respect to the 1st counterbore hole is provided. Is secured. Thus, providing two counterbore holes complicates the structure and leads to an increase in processing cost. Therefore, when the second counterbore hole is omitted and the first counterbore hole is concentrically integrated with the discharge port, the second counterbore hole is omitted, and the first counterbore hole has a large diameter. Need arises. If a large hole diameter of the first counterbore hole is ensured in this way, there is a possibility that the first counterbore hole may interfere with other components. Therefore, the position of the first counterbore hole is determined in consideration of this. When the position of the first counterbore hole is determined, the position of the discharge port provided concentrically with the first counterbore hole is also determined, and the size of the discharge notch is also determined according to the position of the discharge port. For this reason, there has been a problem that it is difficult to achieve both the securing of the counterbore hole diameter necessary for reducing the pressure loss of the refrigerant gas during discharge and the reduction of the discharge notch.

The present invention has been made in view of the above points, and is a hermetic compression capable of achieving both the securing of the counterbore hole diameter necessary for reducing the pressure loss of the refrigerant gas at the time of discharge and the reduction of the discharge notch. An object is to provide a machine and a refrigeration cycle apparatus.

A hermetic compressor according to the present invention includes a cylindrical cylinder that forms a compression chamber that compresses refrigerant by rotation of a crankshaft, and a bearing that is disposed on an end surface in the axial direction of the cylinder and rotatably supports the crankshaft. The bearing has a discharge port for discharging the refrigerant compressed in the compression chamber, and a concave counterbore hole provided around the discharge port and having a volume necessary for the flow of the refrigerant discharged from the discharge port. The discharge port is eccentrically provided on the bearing center side with respect to the counterbore hole, and a discharge notch for communicating the compression chamber and the discharge port is provided on the inner wall portion of the cylinder facing the eccentric discharge port. It is what.

According to the present invention, the counterbore hole is formed in the volume necessary for the flow of the refrigerant discharged from the discharge port, and the discharge port is provided eccentric to the bearing center side with respect to the counterbore hole. It is possible to achieve both the securing of the counterbore hole diameter necessary for reducing the pressure loss of the refrigerant gas and the reduction of the discharge notch.

It is a schematic longitudinal cross-sectional view of the hermetic compressor which concerns on Embodiment 1 of this invention. It is a typical top view of the compression mechanism part of the hermetic compressor concerning Embodiment 1 of this invention. It is a general | schematic sectional drawing of the circumference | surroundings including the bearing of the hermetic compressor which concerns on Embodiment 1 of this invention. 1 is a schematic plan view of a bearing of a hermetic compressor according to Embodiment 1 of the present invention. It is a typical top view of the compression mechanism part of a comparative example. It is a general | schematic sectional drawing of the circumference | surroundings including the bearing of a comparative example. It is a schematic plan view of the bearing of a comparative example. It is a figure which shows the refrigerant circuit of the refrigerating-cycle apparatus which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
1 is a schematic longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. The hermetic compressor according to the first embodiment will be described by taking a two-stage hermetic rotary compressor as an example. However, the present invention is not limited to this, and is not limited to a single-stage or three-stage or more hermetic rotary compression. Is also applicable.
The hermetic compressor includes an electric motor unit 2 and a compression mechanism unit 3 that is coupled to the electric motor unit 2 via a crankshaft 4 and compresses the refrigerant by the rotation of the crankshaft 4. It has an arranged configuration. A suction pipe 5 for sucking gas is connected to the side surface of the sealed container 1, and a discharge pipe 6 for discharging compressed gas is provided on the upper surface of the sealed container 1.

The electric motor unit 2 includes a stator 2a attached to the crankshaft 4 and a rotor 2b that rotationally drives the rotor 2b. Then, the energization of the stator 2 a is started, so that the rotor 2 b is rotated, and the rotational power is transmitted to the compression mechanism unit 3 through the crankshaft 4.

The compression mechanism section 3 includes upper and lower bearings 40, 50 disposed on both axial end surfaces of the first compression mechanism section 30A, the second compression mechanism section 30B, and the first compression mechanism section 30A and the second compression mechanism section 30B. And. Each of the bearings 40 and 50 includes a hollow cylindrical bearing boss portion 40a that rotatably supports the crankshaft 4, and a flat plate-shaped end plate portion 40b that closes an end surface of a cylinder 31 described later. A discharge port 41 is formed in the end plate portion 40b. Further, the intermediate partition plate 7 is disposed between the first compression mechanism 30A and the second compression mechanism 30B.

FIG. 2 is a schematic plan view of the compression mechanism portion of the hermetic compressor according to Embodiment 1 of the present invention. Hereinafter, the configuration of the first compression mechanism 30A and the second compression mechanism 30B of the compression mechanism 3 will be described. Since the first compression mechanism 30A and the second compression mechanism 30B have basically the same configuration, the first compression mechanism 30A will be described below as a representative.

The first compression mechanism portion 30A is slidably disposed in a cylindrical cylinder 31, a rolling piston 32 that is rotatably fitted to the eccentric shaft portion 4a of the crankshaft 4, and a vane groove 35 provided in the cylinder 31. Vane 33 and the like. The cylinder 31 is formed of a flat plate, and a substantially cylindrical through-hole is formed through substantially vertically at the center. The compression hole 34 is formed in the cylinder 31 by closing the through hole by the end plate portion 40 b of the bearing 40 and the intermediate partition plate 7.

The vane groove 35 communicates with the compression chamber 34 and extends in the radial direction of the compression chamber 34, and the vane tip 33 a of the vane 33 movably provided in the vane groove 35 slides on the outer peripheral surface of the rolling piston 32. By contacting, the inside of the compression chamber 34 is divided into a low pressure part 36 and a high pressure part 37. In addition, the cylinder 31 is provided with a suction port 38 that communicates with the low pressure portion 36 and a discharge notch 39 that communicates with a discharge port 41 formed in the end plate portion 40 b of the bearing 40. The discharge notch 39 is formed by cutting the inner wall of the cylinder 31 in accordance with the outer shape of the discharge port 41. That is, the inner wall portion of the cylinder 31 facing the discharge port 41 is notched to form a discharge notch 39, and the compression chamber 34 communicates with the discharge port 41 through the discharge notch 39.

FIG. 3 is a schematic cross-sectional view of the periphery including the bearing of the hermetic compressor according to Embodiment 1 of the present invention. FIG. 4 is a schematic plan view of the bearing of the hermetic compressor according to Embodiment 1 of the present invention.
A recess 60 is formed around the discharge port 41 in the bearing 40. As shown in FIG. 4, the recess 60 includes a circular concave counterbore hole 61 formed around the discharge port 41 and a discharge valve groove 62 extending in one direction from the outer periphery of the counterbore hole 61.

Disposed within the discharge valve groove 62 are a discharge valve 63 that covers the outlet opening of the discharge port 41 and prevents backflow of refrigerant gas, and a valve presser 64 that limits the lift amount of the discharge valve 63, and these are rivets 65. The bearing 40 and the cylinder 31 are fixed. When the fluid is compressed to a predetermined pressure in the compression chamber 34, the discharge valve 63 is lifted against the elastic force and the discharge port 41 is opened. The compressed refrigerant gas is discharged from the opened discharge port 41 into the inner space of the sealed container 1.

Returning to the explanation of FIG. In the first compression mechanism section 30 </ b> A configured as described above, when electric power is supplied to the electric motor section 2, the crankshaft 4 is rotated by the electric motor section 2. As the crankshaft 4 rotates, the eccentric shaft portion 4 a moves eccentrically in the compression chamber 34.

伴い As the eccentric shaft 4a rotates eccentrically, the rolling piston 32 rotates eccentrically in the cylinder 31. Along with the rotation of the rolling piston 32, the low-pressure part 36 into which the low-pressure gas refrigerant has been sucked through the suction port 38 turns to the high-pressure part 37, and the volume of the high-pressure part 37 is gradually reduced to compress the refrigerant. . When the compressed gas refrigerant reaches a predetermined pressure, it is guided to the discharge port 41 through the discharge notch 39 of the cylinder 31 and discharged from the discharge port 41 to the internal space of the sealed container 1.

The second compression mechanism portion 30B is the first compression mechanism in that the member that closes the through hole formed at the approximate center of the cylinder 31 of the second compression mechanism portion 30B is the intermediate partition plate 7 and the bearing 50. Unlike the unit 30A, other configurations and operations are basically the same as those of the first compression mechanism unit 30A.

In the first compression mechanism 30A and the second compression mechanism 30B, the suction and compression of the refrigerant gas are repeated as the crankshaft 4 rotates. Then, the refrigerant gas compressed by each of the first compression mechanism portion 30A and the second compression mechanism portion 30B and discharged to the internal space of the sealed container 1 is discharged from the discharge pipe 6 to the outside of the sealed container 1.

As a characteristic feature of the first embodiment, the discharge port 41 is provided eccentric to the center side of the bearing with respect to the counterbore hole 61. That is, as shown in FIG. 4, the center M <b> 1 of the discharge port 41 is eccentric to the bearing center side with respect to the center M <b> 2 of the counterbore hole 61. The counterbore 61 is configured with a hole diameter that realizes a volume necessary for securing a sufficient space for refrigerant flow immediately after discharge, that is, a hole diameter required for reducing the pressure loss of the refrigerant gas during discharge.

Hereinafter, in order to more clearly describe the effect of this configuration, as a comparative example, a configuration in which the discharge port 41 and the counterbore 61 are formed in concentric circles will be given and described in comparison with this.

First, the configuration of the comparative example will be described with reference to FIGS. FIG. 5 is a schematic plan view of a compression mechanism portion of a comparative example. FIG. 6 is a schematic cross-sectional view of the periphery including the bearing of the comparative example. FIG. 7 is a schematic plan view of a bearing of a comparative example.

5 to 7, there is one counterbore hole 61 formed in the bearing 40, and this one counterbore hole 61 is configured with a hole diameter necessary for reducing the pressure loss of the refrigerant gas at the time of discharge. ing. The counterbore hole 61 and the discharge port 410 are formed concentrically, and the discharge notch 390 is configured to face the discharge port 410 and cut out the inner wall of the cylinder 31.

On the other hand, in the first embodiment, the discharge port 41 is eccentrically provided on the bearing center side with respect to the counterbore hole 61 as described above. As a result, the position of the discharge notch 39 formed on the inner wall of the cylinder 31 in accordance with the position of the discharge port 41 also approaches the bearing center side. As a result, as apparent from a comparison between the discharge notch 39 of the first embodiment shown in FIG. 2 and the discharge notch 390 of the comparative example shown in FIG. The dead volume of 31 can be reduced. That is, in the first embodiment, the discharge notch 39 can be reduced while the counterbore hole 61 is secured to a necessary hole diameter. Therefore, it is possible to achieve both reduction of pressure loss during discharge by securing the hole diameter of the counterbore hole 61 necessary for reducing pressure loss during discharge and reduction of recompression loss and overheat loss due to reduction of the discharge notch 39. is there. As a result, the performance of the hermetic compressor can be improved.

Here, in FIG. 7 of the comparative example, when the position of the discharge port 410 is shifted to the bearing center side, the counterbore hole 61 is provided concentrically with the discharge port 41 in the comparative example. It will be close to the bearing center side. In this case, the counterbore hole 61 interferes with the bearing boss portion 40a. In order to prevent the counterbore 61 from interfering with the bearing boss 40a, it is necessary to reduce the hole diameter of the counterbore 61, and the pressure loss immediately after the high-pressure refrigerant gas is discharged increases.

On the other hand, in the first embodiment, the counterbore hole 61 having a hole diameter necessary for reducing the pressure loss of the refrigerant gas at the time of discharge is disposed at a position that does not cause interference with the bearing boss portion 40a. On the other hand, by making the discharge port 41 eccentric to the bearing center side, both the securing of the hole diameter of the counterbored hole 61 and the reduction of the discharge notch 39 can be achieved.

Embodiment 2. FIG.
The second embodiment relates to a refrigeration cycle apparatus including the hermetic compressor 71 of the first embodiment.

FIG. 8 is a diagram showing a refrigerant circuit of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
The refrigeration cycle apparatus 70 includes the hermetic compressor 71 of the first embodiment, a condenser 72, an expansion valve 73 as a decompression device, and an evaporator 74. The gas refrigerant discharged from the hermetic compressor 71 flows into the condenser 72, exchanges heat with the air passing through the condenser 72, and flows out as high-pressure liquid refrigerant. The high-pressure liquid refrigerant that has flowed out of the condenser 72 is decompressed by the expansion valve 73, becomes a low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator 74. The low-pressure gas-liquid two-phase refrigerant flowing into the evaporator 74 exchanges heat with the air passing through the evaporator 74 to become a low-pressure gas refrigerant, and is sucked into the hermetic compressor 71 again.

The refrigeration cycle apparatus 70 configured as described above includes the hermetic compressor 71 of the first embodiment, so that power consumption can be reduced.

In addition, the refrigeration cycle apparatus 70 can be applied to an air conditioner, a refrigerated freezer, or the like.

1 closed container, 2 motor section, 2a stator, 2b rotor, 3 compression mechanism section, 4 crankshaft, 4a eccentric shaft section, 5 suction pipe, 6 discharge pipe, 7 intermediate partition plate, 13b counterbore section, 30A 1st Compression mechanism, 30B Second compression mechanism, 31 cylinder, 32 rolling piston, 33 vane, 33a vane tip, 34 compression chamber, 35 vane groove, 36 low pressure, 37 high pressure, 38 suction port, 39 discharge notch , 40 bearing, 40a bearing boss, 40b end plate, 41 discharge port, 50 bearing, 60 recess, 61 counter bore, 62 discharge valve groove, 63 discharge valve, 64 valve presser, 65 rivet, 70 refrigeration cycle device, 71 Hermetic compressor, 72 condenser, 73 expansion valve, 74 evaporator, 390 discharge notch, 410 discharge port, Centers of the ejection ports, M2 counterbore center.

Claims

A cylindrical cylinder forming a compression chamber for compressing the refrigerant by rotation of the crankshaft;
A bearing that is disposed on an axial end surface of the cylinder and rotatably supports the crankshaft;
The bearing has a discharge port for discharging the refrigerant compressed in the compression chamber, and a concave counterbore hole provided around the discharge port and having a volume necessary for the flow of the refrigerant discharged from the discharge port. Is formed,
The discharge port is provided eccentric to the bearing center side with respect to the counterbore hole, and a discharge notch communicating the compression chamber and the discharge port is formed in an inner wall portion of the cylinder facing the eccentric discharge port. A hermetic compressor provided.
A refrigeration cycle apparatus comprising the hermetic compressor according to claim 1, a condenser, a decompression device, and an evaporator.