WO2012090345A1

WO2012090345A1 - Refrigerant compressor

Info

Publication number: WO2012090345A1
Application number: PCT/JP2011/003903
Authority: WO
Inventors: 雷人河村; 哲英横山; 英明前山; 白藤　好範
Original assignee: 三菱電機株式会社
Priority date: 2010-12-27
Filing date: 2011-07-07
Publication date: 2012-07-05
Also published as: JP5506953B2; JPWO2012090345A1

Abstract

A refrigerant compressor is provided with a hermetically sealed container (2) and is also provided, within the hermetically sealed container (2), with a motor (9), compression mechanisms (10, 20) which are driven by a drive shaft (7), a lubricating oil suction opening (8) which is provided at the lower end of the drive shaft (7), and a lubricating oil storage section (65) which is provided at the bottom of the hermetically sealed container (2). The refrigerant compressor is further provided with lubricating oil flow paths (77, 78) provided inside the drive shaft so that the lubricating oil (60) stored in the lubricating oil storage section (65) is supplied from the lubrication oil suction opening (8) to the slide sections of the compression mechanisms and to the bearing sections of the drive shaft. The refrigerant compressor is also provided with a partition member (71) for partitioning the lubricating oil storage section (65) into a space along the inner wall of the hermetically sealed container and a space other than the space along the inner wall. An oil supply path leading to the lubricating oil suction opening is formed by the gap between the partition member (71) and the inner wall of the bottom of the hermetically sealed container (2).

Description

Refrigerant compressor

The present invention relates to a refrigerant compressor, and more particularly to a cooling structure for lubricating oil supplied to a sliding portion of a refrigerant compressor, a bearing portion of a drive shaft, and the like.

Conventionally, a vapor compression refrigeration cycle using a rotary compressor has been used in a refrigeration and air-conditioning apparatus such as a refrigerator-freezer, an air conditioner, or a heat pump type water heater. On the other hand, from the viewpoint of preventing global warming, there is a demand for energy saving and efficiency improvement of the vapor compression refrigeration cycle.

In a conventional refrigerant compressor, a compression mechanism that compresses sucked refrigerant from a low pressure to a high pressure, a motor that drives the compression mechanism, and high-temperature lubricating oil stored in the bottom of the sealed container are contained in a high-pressure sealed container. Prepare. As the compressor is driven, the stored lubricating oil is supplied to each drive section through a lubricating oil suction port provided at the lower end of the driving shaft of the compression mechanism, and flows out into the cylinder internal space of the compression mechanism. .

At this time, since the high-temperature lubricating oil is mixed with the refrigerant in the internal space of the cylinder to heat the refrigerant in the cylinder, there is a problem in that heating loss occurs and the compressor efficiency decreases.

Conversely, cooling the lubricating oil supplied to the compression mechanism has the effect of reducing the heating loss and improving the compressor efficiency.

Examples of conventional techniques relating to such cooling of the lubricating oil include the following.
For example, in Patent Document 1, an oil guide / cooling pipe for circulating / cooling lubricating oil is installed outside a sealed container, and one end is a bearing sliding part and the other end is a lubricating oil storage part in the sealed container. It describes a refrigerant compressor adapted to communicate.
In the refrigerant compressor having such a configuration, the lubricating oil is supplied to the bearing sliding portion via the oil guide / cooling pipe outside the sealed container. For this reason, the lubricating oil supplied to the bearing sliding portion can be cooled to reduce the heating loss and improve the compressor efficiency.

In Patent Document 2, in an oil separator / collector attached to the downstream side of the refrigerant compressor, a heat dissipating fin is installed on the outer wall of the oil reservoir of the hermetic container, and oil is returned to the refrigerant compressor by the differential pressure. The structure which arrange | positions the partition member for flowing lubricating oil along the inner wall of an airtight container in an oil sump part is described. This partition member is formed by bending a flat plate into a U-shaped cross section.
In the oil separator / collector having such a configuration, the lubricating oil returned to the refrigerant compressor flows along the inner wall of the sealed container having the heat dissipating fins on the outside, so that the cooling effect of the lubricating oil can be enhanced. it can.

Patent Document 3 proposes an injection-compatible two-stage compression rotary compressor. This two-stage compressor is provided with means for promoting heat exchange between the intermediate pressure injection refrigerant and the inside or the outer surface of the sealed container so that the intermediate pressure injection refrigerant absorbs heat.
According to this configuration, the injection refrigerant absorbs the heat of the discharge gas of the high-stage compression mechanism and the heat loss due to the sliding loss and motor loss generated in the compressor, so that the entire compressor can be cooled. Has been.

Japanese Patent Laid-Open No. 3-175171 (FIG. 6) Japanese Patent Laid-Open No. 10-220380 (FIG. 6) Japanese Patent Laying-Open No. 2008-248865 (FIG. 8)

In the refrigerant compressor described in Patent Document 1, it is necessary to once install an oil guide / cooling pipe that communicates between the lubricating oil reservoir in the sealed container and the bearing sliding part, outside the sealed container. . Therefore, the refrigerant compressor having such a configuration has a problem that the structure is complicated and is not suitable for space saving. On the other hand, Patent Document 2 does not relate to a lubricating oil supply structure in the refrigerant compressor. In the two-stage compressor, in order to expand the injection operation range, it is necessary to uniformly mix the refrigerant discharged from the low-stage compression mechanism and the injection refrigerant so that the refrigerant does not get wet. However, in the two-stage compressor described in Patent Document 3, since the two-phase injection refrigerant is directly injected into the low-stage discharge muffler chamber, the refrigerant is discharged from the low-stage compression mechanism so that the refrigerant does not get wet. There is a problem in uniformly mixing the refrigerant and the injection refrigerant.

The present invention has been made in view of the problems as described above. By reducing the temperature of the lubricating oil supplied to the compression mechanism with a simple structure, the heating loss is reduced and the compressor efficiency is improved. The purpose is to provide a refrigerant compressor.
It is another object of the present invention to provide a refrigerant compressor having a simple lubricating oil cooling structure that can be applied to a two-stage compressor.

A refrigerant compressor according to the present invention includes a sealed container, a motor, a compression mechanism driven by a drive shaft, a lubricating oil suction port provided at a lower end of the drive shaft, A lubricating oil reservoir provided at the bottom of the sealed container,
The lubricating oil stored in the lubricating oil reservoir is provided inside the drive shaft so that the lubricating oil is supplied from the lubricating oil suction port to the sliding portion of the compression mechanism and the bearing portion of the drive shaft. In a refrigerant compressor comprising a lubricating oil flow path,
Installing a partition member that divides the lubricating oil reservoir into a space along the inner wall of the sealed container and a space other than the space;
The oil supply path to the lubricating oil suction port is formed by a gap sandwiched between the partition member and the inner wall of the bottom of the sealed container.

In the refrigerant compressor according to the present invention, the partition member has a temperature distribution in the space along the inner wall of the lubricant and the other space by the partition member, and the lubricant outside the partition member toward the lubricant inlet is radiated from the sealed container. It can be cooled by actively using. For this reason, it is possible to reduce the temperature of the lubricating oil supplied to the compression mechanism with a space-saving and simple structure, thereby reducing the heating loss and improving the compressor efficiency.

It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 2 of this invention. It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 3 of this invention. It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 4 of this invention. It is an enlarged view of the bottom part vicinity of the airtight container of the refrigerant compressor which concerns on Embodiment 5 of this invention. It is explanatory drawing regarding the installation method of the refrigerant compressor which concerns on Embodiment 5 of this invention. It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 6 of this invention. It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 7 of this invention. FIG. 9 is a cross-sectional view taken along the line AA in FIG. It is a figure which shows how to wind the heat insulating material of the refrigerant compressor which concerns on Embodiment 8 of this invention. It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 9 of this invention. It is sectional drawing which shows the whole structure of the refrigerant compressor which concerns on Embodiment 10 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. Here, as a refrigerant compressor, a two-cylinder compressor having two upper and lower compression mechanism portions, that is, an upper compression mechanism portion and a lower compression mechanism portion will be described as an example, but the present invention is not limited to this. Needless to say. 1 to 12, the same reference numerals denote the same or equivalent parts, and this is common throughout the entire specification.

Embodiment 1 FIG.
FIG. 1 is a cross-sectional view showing a configuration of a refrigerant compressor 1 according to Embodiment 1 of the present invention. The black arrows in the figure indicate the flow of the refrigerant, and the white arrows indicate the flow of the lubricating oil 60.
A refrigerant compressor 1 according to Embodiment 1 compresses a refrigerant to a high temperature and a high pressure, and includes a sealed container 2 that is a high pressure container. Inside the sealed container 2, an upper compression mechanism unit 10, a lower compression mechanism unit 20, an intermediate partition member 30, an upper support member 40, a lower support member 50, an upper discharge muffler container 42, a lower discharge muffler container 52, Lubricating oil 60, drive shaft 7, and motor 9 are provided.

Lower discharge muffler container 52, lower support member 50, lower compression mechanism part 20, intermediate partition member 30, upper compression mechanism part 10, upper support member 40, upper discharge muffler container 42, motor 9 are stacked in order from the lower side in the axial direction of the drive shaft 7. Each of the upper support member 40 and the lower support member 50 includes an upper bearing portion 41 and a lower bearing portion 51 that rotatably support the drive shaft 7. Further, a lubricating oil reservoir 65 for storing the lubricating oil 60 is provided at the bottom of the hermetic container 2, and the lubricating oil 60 is disposed at the lower end of the drive shaft 7 at each sliding portion of the compression mechanism and the upper bearing of the drive shaft 7. Lubricating oil intake port 8 for supplying to part 41 and lower bearing part 51 is provided. The lubricating oil supply flow path includes a lubricating oil suction port 8, a lubricating oil flow channel 77 extending in the axial direction from the lubricating oil suction port 8 through the drive shaft 7, and a radial direction extending from the lubricating oil flow channel 77. A communication port 78 communicating with each sliding portion of the mechanism portion and the upper bearing portion 41 and the lower bearing portion 51 of the drive shaft 7 is provided.

The sealed container 2 has a vertical shape having end plates on the upper and lower surfaces of the cylindrical body. The lower part of the hermetic container 2 is fixed to a bottom plate 82 of the outdoor unit via a support leg 80 and an anti-vibration rubber 81. The refrigerant compressor 1 is entirely surrounded by a heat insulating enclosure 85, and the refrigerant suction pipe 3 and the discharge pipe 4 protrude from the heat insulating enclosure 85. A fan 101 that forcibly circulates air in the external space is provided outside the heat insulating enclosure 85.

The upper compression mechanism unit 10 and the lower compression mechanism unit 20 are provided with

cylinders

11 and 21 and

rotary pistons

12 and 22, respectively.
The upper compression mechanism unit 10 is stacked such that the cylinder 11 is sandwiched between the upper support member 40 and the intermediate partition member 30. The lower compression mechanism unit 20 is stacked such that the cylinder 21 is sandwiched between the lower support member 50 and the intermediate partition member 30.
The

rotary pistons

12 and 22 are respectively mounted on the eccentric portions of the drive shaft 7, and perform eccentric rotational motion by rotation of the drive shaft 7 driven to rotate by the motor 9 inside the corresponding

cylinders

11 and 21, respectively. As a result, the refrigerant is sucked, and the sucked refrigerant is compressed and discharged. The refrigerant is sucked into the

respective cylinders

11 and 21 from the suction pipe 3 via the suction muffler 5 and the cylinder suction pipe 6.

The refrigerant compressed by the upper compression mechanism unit 10 is discharged from the upper discharge port 44 into the upper discharge muffler container 42 by opening the upper discharge valve 43, and is further sealed from an opening 45 provided in the upper discharge muffler container 42. 2 is discharged into the upper space.
Further, the refrigerant compressed by the lower compression mechanism unit 20 is discharged from the lower discharge port 54 into the lower discharge muffler container 52 by opening the lower discharge valve 53, and further, the lower support member 50, the intermediate partition The refrigerant is discharged into the upper discharge muffler container 42 through the connection flow path 31 penetrating the member 30 and the upper support member 40, and merged with the discharge refrigerant discharged from the upper compression mechanism unit 10 through the opening 45 in the sealed container 2. It is discharged into the upper space.

The refrigerant compressor 1 further includes a partition member 71 that divides the lubricating oil 60 stored at the bottom of the hermetic container 2 into an inner space 61 and an outer space 62. The shape of the partition member 71 is not particularly limited, but it is preferable to form the partition member 71 in a cup shape having a through hole at the bottom. Here, the main flow of the oil supply path toward the lubricating oil intake port 8 is formed by a gap sandwiched between the sealed container 2 and the partition member 71. The partition member 71 and the lower discharge muffler container 52 are provided with through

holes

71a and 52a communicating with the lubricating oil suction port 8, respectively.

Next, operation | movement of the refrigerant compressor 1 of Embodiment 1 is demonstrated.
First, electric power is supplied to the motor 9 and the motor 9 is driven. As a result, the drive shaft 7 rotates, and the refrigerant passes through the suction muffler 5 from the suction pipe 3 and is sucked into the upper compression mechanism unit 10 and the lower compression mechanism unit 20. The refrigerant sucked into the upper compression mechanism unit 10 and the lower compression mechanism unit 20 is compressed from a low pressure to a high pressure and is discharged into the sealed container 2. The refrigerant discharged to the inside of the sealed container 2 is discharged from the discharge pipe 4 to the outside of the sealed container 2 through the gaps of the motor 9 (between the rotor and the stator and between the stator and the sealed container 2). The refrigerant discharged from the refrigerant compressor 1 passes through a condenser, an expansion mechanism, and an evaporator (not shown) and is again sucked into the refrigerant compressor 1 from the suction pipe 3. Thereby, a refrigerating cycle is formed by refrigerant compressor 1, a condenser, an expansion mechanism, and an evaporator.

During this operation, the lubricating oil 60 stored at the bottom of the sealed container 2 flows to the lubricating oil suction port 8 through a gap sandwiched between the sealed container 2 and the partition member 71, and the drive shaft is driven by the lubricating oil suction port 8. 7 is taken into the lubricating oil flow path 77 from the lower end of 7. Thereafter, oil is supplied to each sliding portion of the compression mechanism portion by the differential pressure, and flows out into the internal space of the

cylinders

11 and 21. Further, the lubricating oil 60 is also supplied to the upper bearing portion 41 and the lower bearing portion 51 of the drive shaft 7, thereby preventing problems such as seizure of the compression mechanism portion and the bearing portion. A part of the lubricating oil 60 supplied to the lubricating oil flow path 77 is discharged to the outside of the apparatus together with the refrigerant, but the remaining part is collected in the lubricating oil storage unit 65.

Thus, since the lubricating oil 60 directed to the lubricating oil suction port 8 flows along the inner wall of the sealed container 2, it is cooled by actively utilizing the heat radiation of the sealed container 2. Thereby, temperature distribution is made in the inner space 61 and the outer space 62 of the lubricating oil 60, and only the lubricating oil 60 heading toward the lubricating oil suction port 8 is preferentially cooled. Therefore, in the refrigerant compressor 1 according to Embodiment 1, it is possible to reduce the heating loss and improve the compressor efficiency.

In the refrigerant compressor 1 according to the first embodiment, the minute gap 100 is provided between the partition member 71 and the lower discharge muffler container 52. Accordingly, the lubricating oil 60 in the inner space 61 flows out to the outer space 62 through the gap 100.

For this reason, even when the oil surface height of the lubricating oil 60 decreases, the lubricating oil 60 accumulated in the inner space 61 flows out to the outer space 62 through the gap 100, so that the lubricating oil 60 in the outer space 62 is depleted. Can be prevented. However, the lubricating oil 60 that flows out from the gap 100 has a higher temperature than the lubricating oil 60 that is cooled through the flow path sandwiched between the sealed container 2 and the partition member 71. Therefore, if the flow rate of the lubricating oil 60 flowing out from the gap 100 is large, the cooling effect of the lubricating oil 60 supplied from the lubricating oil suction port 8 is impaired, so the flow rate needs to be limited. That is, the gap 100 is a flow path for limiting the flow rate of the lubricating oil 60 flowing out from the inner space 61 to the outer space 62 to a small amount. Therefore, while the refrigerant compressor 1 is in operation, the lubricating oil 60 is supplied to the oil supply path little by little from the gap (flow path) 100, but this does not impair the cooling effect of the lubricating oil 60. Further, if the partition member 71 is cup-shaped, the lubricating oil 60 can be stored inside, so this action can be performed effectively, and therefore, the lubricating oil 60 is prevented from being depleted in the oil supply path. In addition, the lubricating oil 60 can be cooled. The gap (flow path) 100 is provided between the partition member 71 and the lower discharge muffler container 52 in the first embodiment, but one compression mechanism section without the lower compression mechanism section 20 is provided. When it has, it is provided between the partition member 71 and the drive shaft 7.

Embodiment 2. FIG.
FIG. 2 is a cross-sectional view illustrating a configuration of the refrigerant compressor 1 according to Embodiment 2.
In the following, the configuration of the refrigerant compressor 1 shown in FIG. 2 will be described mainly with respect to the differences from the refrigerant compressor 1 shown in FIG.
In the refrigerant compressor 1 according to the second embodiment, the outer space 62 divided by the partition member 71 is connected to the vane back pressure chamber 14 of the upper compression mechanism unit 10 and the lower compression mechanism unit 20 via the connection channel 72. 24 is in communication. That is, the connecting flow path 72 communicates from the outer space 62 to the vane back pressure chamber 24 of the lower compression mechanism portion 20, and further passes through the intermediate partition member 30 from the vane back pressure chamber 24 to the upper compression mechanism portion 10. It is formed by an independent flow path communicating with the vane back pressure chamber 14. Further, the opening portions of the vane back

pressure chambers

14, 24 communicating with the vane back

pressure chambers

14, 24 and the inside of the sealed container 2 are closed by sealing

materials

17, 27. Furthermore, a heat radiating fin 91 is provided on the outer wall surface of the lubricating oil reservoir 65 of the sealed container 2. In the figure, 15 and 25 are vanes, and 16 and 26 are springs.

In the refrigerant compressor 1 according to the second embodiment, in addition to the lubricating oil 60 directed to the lubricating oil suction port 8, the lubricating oil supplied to the sliding portions of the

vanes

15 and 25 is also cooled. Further, the heat radiation of the lubricating oil 60 is further promoted by the heat radiation fins 91 installed on the outer wall surface of the lubricating oil reservoir 65 of the sealed container 2.
Therefore, according to the second embodiment, it is possible to further reduce the heating loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the first embodiment.

Embodiment 3 FIG.
FIG. 3 is a cross-sectional view illustrating a configuration of the refrigerant compressor 1 according to Embodiment 3.
In the following, the configuration of the refrigerant compressor 1 shown in FIG. 3 will be described mainly with respect to the differences from the refrigerant compressor 1 shown in FIG.
In the refrigerant compressor 1 according to the third embodiment, a hollow shape 92 is provided at the bottom of the sealed container 2 in the vicinity of the lubricating oil inlet 8. The lower end portion of the drive shaft 7 is disposed inside the hollow shape 92. Further, the refrigerant compressor 1 is surrounded by a heat insulating enclosure 86 so as to avoid the hollow shape 92. That is, the hollow shape 92 is exposed to the outside from the heat insulating enclosure 86.

The lubricating oil suction port 8 at the lower end of the drive shaft 7 is provided with an oil cap 89 that assists the centrifugal pump action of sucking up the lubricating oil 60 using the rotation of the drive shaft 7, and the oil cap 89 is surrounded by a hollow shape 92. It is arranged so that it is located in the space. A communication port 78 that communicates with the internal space of the sealed container 2 is provided at the upper end of the lubricating oil passage 77 of the drive shaft 7 that is hollow. Of the lubricating oil 60 sucked up by the oil cap 89, most of the lubricating oil 60 that has not been supplied with differential pressure to each sliding portion is returned again to the lubricating oil reservoir 65 of the sealed container 2 through the communication port 78.
For this reason, the circulation amount of the lubricating oil 60 in the refrigerant compressor 1 is increased by the power of the oil cap 89. As a result, the flow velocity of the lubricating oil 60 toward the lubricating oil suction port 8 increases.

In the refrigerant compressor 1 according to the third embodiment, the concave shape 92 is exposed outside the heat insulating enclosure 86 that is forced convection by the fan 101, so that the lubricating oil 60 accumulated in the concave shape 92 is effectively removed. Cooling. Further, the installation of the oil cap 89 increases the flow rate of the lubricating oil 60 toward the lubricating oil suction port 8, so that the heat transfer of the lubricating oil 60 is promoted.
Therefore, according to the third embodiment, it is possible to further reduce the heating loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the first embodiment.

In the refrigerant compressor 1 according to Embodiment 3, a plurality of lubricating oil relief holes 74 that communicate the inner space 61 and the outer space 62 in the radial direction are provided in the lower part of the side surface of the partition member 73 formed in a cup shape. Yes. Further, the cross-sectional area and the number of the lubricating oil relief holes 74 are determined so that the flow resistance at the lubricating oil relief holes 74 is sufficiently larger than the resistance of the flow path sandwiched between the partition member 73 and the sealed container 2. It is assumed that the flow rate of the lubricating oil 60 passing through the lubricating oil relief hole 74 is limited.

In the refrigerant compressor 1 according to the third embodiment, the lubricating oil relief hole 74 is provided in the lower part of the side surface of the cup-shaped partition member 73, so that even when the oil level height of the lubricating oil 60 is lowered, the internal space 61 is provided. Since the lubricating oil 60 is accumulated, the lubricating oil 60 in the outer space 62 can be prevented from being depleted. Further, even when the internal space 61 and the external space 62 are communicated with each other by the lubricating oil escape hole 74 as described above, the lubricating oil relief hole 74 is disposed sufficiently away from the lubricating oil suction port 8, and the lubricating oil escape is performed. By limiting the flow rate of the lubricating oil 60 through the hole 74, the cooling effect of the lubricating oil 60 is hardly lowered.
Therefore, according to the third embodiment, it is possible to further reduce the heating loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the first embodiment.

Embodiment 4 FIG.
FIG. 4 is a cross-sectional view illustrating a configuration of the refrigerant compressor 1 according to Embodiment 4.
In the following, the configuration of the refrigerant compressor 1 shown in FIG. 4 will be mainly described with respect to portions different from the refrigerant compressor 1 shown in FIG. In the refrigerant compressor 1 according to the fourth embodiment, the heat radiation fins 93 are provided on the outer wall surface of the recess 92.

In the refrigerant compressor 1 according to the fourth embodiment, the cooling effect of the lubricating oil 60 accumulated in the hollow shape 92 is further promoted by providing the heat sink fins 93 in the hollow shape 92.
Therefore, according to the fourth embodiment, it is possible to further reduce the heating loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the third embodiment.

Embodiment 5 FIG.
FIG. 5 is a cross-sectional view showing the configuration of the refrigerant compressor 1 according to the fifth embodiment.
In the following, the configuration of the refrigerant compressor 1 shown in FIG. 5 will be mainly described with respect to the differences from the refrigerant compressor 1 shown in FIG. In the refrigerant compressor 1 according to the fifth embodiment, the support leg 83 is in close contact with the bottom of the hermetic container 2 so as to cover the vicinity of the lubricating oil inlet 8, and the heat radiation fin 84 is provided at the tip of the support leg 83. Further, the heat dissipating fins 84 are disposed outside the heat insulating enclosure 87.

In the refrigerant compressor 1 according to the fifth embodiment, the sealed container 2 is composed of two members, an upper container 2a and a lower container 2b. FIG. 6 is an enlarged view of the vicinity of the bottom of the lower container 2b of FIG. In the refrigerant compressor 1 according to Embodiment 5, the inner wall of the lower container 2b has an uneven shape.

In the refrigerant compressor 1 according to the fifth embodiment, the lubricating oil 60 in the vicinity of the lubricating oil inlet 8 is used by utilizing heat transfer to the support legs 83 provided with the heat dissipating fins 84 disposed outside the heat insulating enclosure 87. Is further cooled. Furthermore, the inner wall surface of the lower container 2b of the oil supply path to the lubricating oil suction port 8 is formed into an uneven shape, thereby promoting the turbulent flow of the lubricating oil 60 and promoting heat transfer.
Therefore, according to the fifth embodiment, it is possible to further reduce the heat loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the first embodiment.

Generally, such a cup-shaped lower container 2b is manufactured by drawing, and is welded and fixed to the upper container 2a by welding. Therefore, as in the refrigerant compressor 1 according to the fifth embodiment, in order to make the inner wall of the lower container 2b have an uneven shape, for example, a drawing process may be performed using a plate material whose surface has an uneven shape in advance.

Embodiment 6 FIG.
FIG. 7 is a cross-sectional view illustrating a configuration of the refrigerant compressor 1 according to Embodiment 6. In FIG.
In the following, the configuration of the refrigerant compressor 1 shown in FIG. 7 will be mainly described with respect to portions different from the refrigerant compressor 1 shown in FIG. In the refrigerant compressor 1 according to the sixth embodiment, a heat radiating fin 88 is installed at the bottom of the sealed container 2. Similarly to the third embodiment, the refrigerant compressor 1 is surrounded by a heat insulating enclosure 86 so as to avoid the heat radiation fins 88.

In the refrigerant compressor 1 according to the sixth embodiment, the lubricating oil 60 in the vicinity of the lubricating oil inlet 8 is further cooled by the heat dissipating fins 88 exposed to the outside of the heat insulating enclosure 86 that is forced convection by the fan 101. .
Therefore, according to the sixth embodiment, it is possible to further reduce the heating loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the first embodiment.

Embodiment 7 FIG.
FIG. 8 is a cross-sectional view illustrating a configuration of the refrigerant compressor 1 according to Embodiment 7. In FIG.
In the following, the configuration of the refrigerant compressor 1 shown in FIG. 8 will be described mainly with respect to the differences from the refrigerant compressor 1 shown in FIG. In the refrigerant compressor 1 according to Embodiment 7, the upper end of the partition member 76 has a height near the oil level of the lubricating oil 60. The height of the oil level of the lubricating oil 60 is controlled by a control device (not shown) controlling the compressor inflow amount of the lubricating oil 60 based on a detection signal from an oil level gauge (not shown). The

FIG. 9 is a cross-sectional view of the AA cross section of the refrigerant compressor 1 shown in FIG. In the cylinder 21 of the lower compression mechanism portion 20, the clearance between the cylinder 21 and the sealed container 2 is reduced by the circumferential range 95 in the vicinity of the vane 25 storage portion and the suction port 28, and the other circumferential range. In 96, the gap is increased. The cup-shaped partition member 76 has a shape that avoids the circumferential range 95 so as not to interfere with the arrangement of the compression mechanism portion. That is, the part of the partition member 76 in the range 95 is cut off. For this reason, the vane back pressure chamber 24 communicates with the outer space 62. The upper compression mechanism unit 10 has the same configuration.

Further, similarly to the refrigerant compressor 1 according to the third embodiment, a plurality of lubricating oil relief holes 74 that communicate the inner space 61 and the outer space 62 in the radial direction are provided in the lower part of the side surface of the partition member 73.

In the refrigerant compressor 1 according to the seventh embodiment, in addition to the lubricating oil 60 directed to the lubricating oil suction port 8, the lubricating oil supplied to the sliding portions of the

vanes

15 and 25 is also cooled. Furthermore, since the upper end of the partition member 76 is set to a height near the oil level of the lubricating oil 60, heat transfer from the outer space 62 to the inner space 61 is suppressed, and transmission through the oil supply path to the lubricating oil suction port 8 is suppressed. The heat area can be increased. For this reason, the cooling effect of the lubricating oil 60 is increased.
Therefore, according to the seventh embodiment, it is possible to further reduce the heating loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the first embodiment.

Embodiment 8 FIG.
FIG. 10 is a cross-sectional view illustrating a configuration of the refrigerant compressor 1 according to Embodiment 8. In FIG.
In the following, the configuration of the refrigerant compressor 1 shown in FIG. 10 will be mainly described with respect to portions different from the refrigerant compressor 1 shown in FIG. In general, in a refrigerant compressor used in a heat pump water heater or an air conditioner, a heat insulating material 97 such as a quinol carbon fiber is wound around the entire body of the compressor for heat insulation.
On the other hand, in the refrigerant compressor 1 according to the eighth embodiment, the heat insulating material 97 is wound only around the upper region 98 and the suction muffler 5 of the hermetic container 1 and corresponds to the periphery of the partition member 71 (lubricating oil reservoir 65). The heat insulating material 97 is not wound around the lower region 99.

In the refrigerant compressor 1 according to Embodiment 8, the lubricating oil 60 in the vicinity of the lubricating oil suction port 8 is cooled by promoting heat dissipation in the lower region 99 while maintaining heat insulation in the upper region 98.
Therefore, according to the eighth embodiment, it is possible to further reduce the heating loss and improve the compressor efficiency as compared with the refrigerant compressor 1 according to the first embodiment.

In the above embodiment, when a material having high thermal conductivity is used for the sealed container 2, the cooling effect of the lubricating oil 60 can be increased. Similarly, when a material having low thermal conductivity is used for the

partition members

71, 73, 76, heat transfer from the inner space 61 to the outer space 62 in the lubricating oil 60 can be suppressed. The cooling effect of 60 can be increased.

In the above embodiment, the two-cylinder compressor has been described. However, the same effect can be obtained in various refrigerant compressors having different compression mechanisms such as a single cylinder compressor and a two-stage compressor.

In the above embodiment, the rotary piston type refrigerant compressor has been described. However, for example, the same effect can be obtained in various refrigerant compressors having different compression types, such as a swing piston type and a sliding vane type.

Furthermore, when the lubricating oil cooling structure of the present invention is applied to a two-stage compressor, in addition to the effects described in Embodiments 1 to 8, a new improvement effect specific to the two-stage compressor can be obtained. In

Embodiments

9 and 10 described below, an improvement effect when the lubricating oil cooling structure of the present invention is applied to a two-stage compressor will be described.

Embodiment 9 FIG.
FIG. 11 is a cross-sectional view showing a configuration of the refrigerant compressor 1 according to Embodiment 9 of the present invention.
The refrigerant compressor 1 according to Embodiment 9 includes a sealed container 2 that is a high-pressure container. Inside the hermetic container 2, a low-stage compression mechanism 110, a high-stage compression mechanism 120, an intermediate partition member 130, a low-stage support member 140, a high-stage support member 150, a low-stage discharge muffler outer container 146, a low-stage discharge A muffler inner container 147, a high-stage discharge muffler container 152, a lubricating oil 60, a drive shaft 7, and a motor 9 are provided.

Low-stage discharge muffler outer container 146, low-stage discharge muffler inner container 147, low-stage support member 140, low-stage compression mechanism 110, intermediate partition member 130, high-stage compression mechanism 120, and high-stage support The member 150, the high-stage discharge muffler container 152, and the motor 9 are stacked in order from the lower side in the axial direction of the drive shaft 7. Each of the low-stage support member 140 and the high-stage support member 150 includes a low-stage bearing portion 141 and a high-stage bearing portion 151 that rotatably support the drive shaft 7. Further, a lubricating oil reservoir 65 for storing the lubricating oil 60 is provided at the bottom of the hermetic container 2, and the lubricating oil 60 is disposed at the lower end of the driving shaft 7 at each sliding portion of the compression mechanism and the lower stage of the driving shaft 7. A lubricating oil suction port 8 is provided to supply to the bearing portion 141 and the high stage bearing portion 151. The lubricating oil supply flow path includes a lubricating oil suction port 8, a lubricating oil flow channel 77 extending in the axial direction from the lubricating oil suction port 8 through the drive shaft 7, and a radial direction extending from the lubricating oil flow channel 77. A communication port 78 communicating with each sliding portion of the mechanism portion and the upper bearing portion 41 and the lower bearing portion 51 of the drive shaft 7 is provided.

The low-stage compression mechanism 110 and the high-stage compression mechanism 120 are provided with

cylinders

111 and 121 and

rotary pistons

112 and 122, respectively.
The low-stage compression mechanism 110 is stacked such that the cylinder 111 is sandwiched between the low-stage support member 140 and the intermediate partition member 130. The high-stage compression mechanism 120 is stacked such that the cylinder 121 is sandwiched between the high-stage support member 150 and the intermediate partition member 130.
The

rotary pistons

112 and 122 are respectively attached to the eccentric portions of the drive shaft 7, and perform eccentric rotational motion by the rotation of the drive shaft 7 driven to rotate by the motor 9 inside the corresponding

cylinders

11 and 21, respectively. As a result, the refrigerant is sucked, and the sucked refrigerant is compressed and discharged.

Also, the low stage discharge muffler outer container 146 is provided with an injection inlet 160 for introducing an injection refrigerant. The injection refrigerant introduction pipe passes through the sealed container 2 and is connected to the low-stage discharge muffler outer container 146. The low-stage discharge muffler inner container 147 is provided with a communication port 145 for introducing an injection refrigerant therein.

The flow of the refrigerant will be described.
The low-pressure refrigerant sucked from the suction pipe 3 is first sucked into the cylinder 111 of the low-stage compression mechanism 110 via the suction muffler 5 and the cylinder suction pipe 6.
Then, the refrigerant compressed to the intermediate pressure by the low-stage compression mechanism 110 is discharged from the low-stage discharge port 144 into the low-stage discharge muffler inner container 147 by opening the low-stage discharge valve 143.

On the other hand, the refrigerant that has flowed in from the injection inlet 160 passes through the gap space 148 between the low-stage discharge muffler outer container 146 and the low-stage discharge muffler inner container 147 and heads for the communication port 145. At this time, the injection refrigerant is heated by the oil accumulated in the inner space 61 via the low-stage discharge muffler outer container 147. The heated injection refrigerant flows into the low-stage discharge muffler inner container 147 through the communication port 145.
The refrigerant flowing in from the communication port 145 and the refrigerant compressed by the low-stage compression mechanism 110 and discharged from the low-stage discharge port 144 are mixed in the low-stage discharge muffler inner container 147, and the low-stage support member 140, the high-stage compression mechanism 120 is sucked through the intermediate connection flow path 131 that penetrates the low-stage cylinder 111 and the intermediate partition member 130.

The refrigerant compressed to a high pressure by the high-stage compression mechanism 120 is discharged from the high-stage discharge port 154 into the high-stage discharge muffler container 152 by opening the high-stage discharge valve 153, and from the communication port 155 to the inside of the sealed container 2. It is discharged into the upper space.

The refrigerant compressor 1 further includes a partition member 71 that divides the lubricating oil 60 stored at the bottom of the hermetic container 2 into an inner space 61 and an outer space 62. The shape of the partition member 71 is not particularly limited, but it is preferable to form the partition member 71 in a cup shape having a through hole at the bottom. Here, the main flow of the oil supply path toward the lubricating oil intake port 8 is formed by a gap sandwiched between the sealed container 2 and the partition member 71. The partition member 71 is provided with a through hole 71 a that communicates with the lubricating oil suction port 8.

Next, the operation of the refrigerant compressor 1 according to the ninth embodiment will be described.
First, electric power is supplied to the motor 9 and the motor 9 is driven. As a result, the drive shaft 7 rotates, and the refrigerant passes through the suction muffler 5 from the suction pipe 3 and is sucked into the low-stage compression mechanism 110. The refrigerant sucked into the low-stage compression mechanism unit 110 is compressed from a low pressure to an intermediate pressure and mixed with the refrigerant flowing in from the injection inlet 160, and then the mixed refrigerant passes through the intermediate connection flow path 131 and then the high-stage compression mechanism unit. 120 is inhaled. The refrigerant sucked into the high-stage compression mechanism 120 is compressed from an intermediate pressure to a high pressure and is discharged into the sealed container 2. The refrigerant discharged to the inside of the sealed container 2 is discharged from the discharge pipe 4 to the outside of the sealed container 2 through the gaps of the motor 9 (between the rotor and the stator and between the stator and the sealed container 2).

cylinders

111 and 121. Further, the lubricating oil 60 is also supplied to the low-stage bearing portion 141 and the high-stage bearing portion 151 of the drive shaft 7 to prevent the occurrence of problems such as seizure of the compression mechanism portion and the bearing portion. A part of the lubricating oil 60 supplied to the lubricating oil flow path 77 is discharged to the outside of the apparatus together with the refrigerant, but the remaining part is collected in the lubricating oil storage unit 65.

Thus, since the lubricating oil 60 directed to the lubricating oil suction port 8 flows along the inner wall of the sealed container 2, it is cooled by actively utilizing the heat radiation of the sealed container 2. Thereby, temperature distribution is made in the inner space 61 and the outer space 62 of the lubricating oil 60, and only the lubricating oil 60 heading toward the lubricating oil suction port 8 is preferentially cooled. Therefore, the refrigerant compressor 1 according to Embodiment 9 can reduce the heating loss and improve the compressor efficiency in the same manner as the refrigerant compressor 1 according to Embodiment 1.

In the refrigerant compressor 1 according to the ninth embodiment, a temperature distribution is generated in the inner space 61 and the outer space 62 of the lubricating oil 60, and the temperature of the lubricating oil 60 is higher in the inner space 61 than in the outer space 62. . For this reason, the lubricating oil 60 in the inner space 61 can effectively heat the injection refrigerant flowing in the gap space 148 between the low-stage discharge muffler outer container 146 and the low-stage discharge muffler inner container 147. As a result, since the dryness of the injection refrigerant increases, it becomes easy to uniformly mix the injection refrigerant and the refrigerant compressed by the low stage compression mechanism unit 110 without getting wet, and the injection operation range can be expanded.

In the ninth embodiment, a two-stage compressor having a configuration in which the low-stage compression mechanism unit is disposed below the high-stage compression mechanism unit has been described. In the tenth embodiment, a two-stage compressor having a configuration in which a low-stage compression mechanism section is arranged on the upper side of a high-stage compression mechanism section will be described.

Embodiment 10 FIG.
FIG. 12 is a cross-sectional view showing the configuration of the refrigerant compressor 1 according to Embodiment 10 of the present invention. The refrigerant compressor 1 according to Embodiment 10 includes a sealed container 2 that is a high-pressure container. Inside the hermetic container 2, a low-stage compression mechanism 110, a high-stage compression mechanism 120, an intermediate partition member 130, a low-stage support member 140, a high-stage support member 150, a low-stage discharge muffler container 142, and a high-stage discharge muffler A container 152, a lubricating oil 60, a drive shaft 7, and a motor 9 are provided.

Regarding the configuration of the refrigerant compressor 1 according to the tenth embodiment, differences from the refrigerant compressor 1 according to the ninth embodiment will be mainly described.
The refrigerant compressor 1 according to the tenth embodiment includes a high-stage discharge muffler container 152, a high-stage support member 150, a high-stage compression mechanism 120, an intermediate partition member 130, and a low-stage compression. The mechanism unit 110, the low stage support member 140, the low stage discharge muffler container 142, and the motor 9 are stacked in order from the lower side in the axial direction of the drive shaft 7.

The injection inlet 160 for introducing the injection refrigerant is provided in the low-stage discharge muffler container 142. The injection refrigerant introduction pipe passes through the sealed container 2 and is connected to the low-stage discharge muffler container 142. Further, a second connection channel 132 is provided through the high stage support member 150, the high stage cylinder 121, the intermediate partition member 130, the low stage cylinder 111, and the low stage support member 140. Therefore, the high-pressure refrigerant compressed by the high-stage compression mechanism 120 is discharged into the high-stage muffler container 152 and then discharged into the upper space of the sealed container 2 through the second connection flow path 132. .

Thus, in the refrigerant compressor 1 according to Embodiment 10, the high-stage compression mechanism 120 is disposed below the low-stage compression mechanism 110. For this reason, the high-temperature and high-pressure refrigerant in the high-stage discharge muffler container 152 is configured to heat the lubricating oil 60.
However, since the lubricating oil 60 is partitioned into the inner space 61 and the outer space 62 by the partition member 71, the refrigerant in the high-stage discharge muffler container 152 is changed to the lubricating oil 60 in the outer space 62 toward the lubricating oil suction port 8. The effect of suppressing heat transfer is obtained. Therefore, in the refrigerant compressor 1 according to Embodiment 10, it is possible to reduce the heating loss and improve the compressor efficiency.

Embodiments 9 and 10 have described the refrigerant compressor having a configuration in which the intermediate connection channel 131 that communicates the low-stage compression mechanism 110 and the high-stage compression mechanism 120 is inside the hermetic container 2. However, for example, the same effect can be obtained when the intermediate connection channel passes outside the sealed container.

In Embodiments 1 to 10, the rotary piston type refrigerant compressor has been described. However, for example, the same effect can be obtained in various refrigerant compressors having different compression types, such as a swing piston type and a sliding vane type.

1 refrigerant compressor, 2 sealed container, 2a upper container, 2b lower container, 3 suction pipe, 4 discharge pipe, 5 suction muffler, 6 cylinder suction pipe, 7 drive shaft, 8 lubricating oil suction port, 9 motor, 10 upper side Compression mechanism, 20 Lower compression mechanism, 11, 21 Cylinder, 12, 22 Rotating piston, 14, 24 Vane back pressure chamber, 15, 25 Vane, 16, 26 Spring, 17, 27 Sealing material, 28 Inlet , 30 Intermediate partition member, 31 Connecting flow path, 40 Upper support member, 41 Upper bearing portion, 42 Upper discharge muffler container, 43 Upper discharge valve, 44 Upper discharge port, 45 Opening, 50 Lower support member, 51 Lower bearing Part, 52 lower discharge muffler container, 53 lower discharge valve, 54 lower discharge port, 60 lubricating oil, 61 inner space, 62 outer 65, lubricating oil reservoir, 71 partition member, 72 connection channel, 73 partition member, 74 lubricant release hole, 76 partition member, 77 lubricant channel, 78 communication port, 80 support leg, 81 anti-vibration rubber, 82 bottom plate, 83 support legs, 84 heat radiation fin, 85 heat insulation enclosure, 86 heat insulation enclosure, 87 heat insulation enclosure, 88 heat radiation fin, 89 oil heat cap, 91 heat radiation fin, 92 hollow shape, 93 heat radiation fin, 95 range, 96 range, 97 heat insulating material, 98 upper region, 99 lower region, 100 gap, 101 fan, 110 low stage compression mechanism part, 120 high stage compression mechanism part, 111, 121 cylinder, 112, 122 rotating piston, 114, 124 Vane back pressure chamber, 115, 125 vane, 116, 126 spring, 117, 12 Sealing material, 128 inlet, 130 intermediate partition member, 131 intermediate connection channel, 132 second connection channel, 140 low stage support member, 141 low stage bearing, 142 low stage discharge muffler container, 143 low stage discharge Valve, 144 Low stage discharge port, 145 communication port, 146 Low stage discharge muffler outer container, 147 Low stage discharge muffler inner container, 148 clearance space, 149 communication port, 150 High stage support member, 151 High stage bearing part, 152 High Stage discharge muffler container, 153, high stage discharge valve, 154, high stage discharge port, 160 injection inlet.

Claims

A sealed container, a motor, a compression mechanism driven by a drive shaft, a lubricating oil inlet provided at the lower end of the drive shaft, and a lubrication provided at the bottom of the sealed container inside the sealed container An oil reservoir,
The lubricating oil stored in the lubricating oil reservoir is provided inside the drive shaft so that the lubricating oil is supplied from the lubricating oil suction port to the sliding portion of the compression mechanism and the bearing portion of the drive shaft. In a refrigerant compressor comprising a lubricating oil flow path,
Installing a partition member that divides the lubricating oil reservoir into a space along the inner wall of the sealed container and a space other than the space;
An oil supply path to the lubricating oil suction port is formed by a gap sandwiched between the partition member and an inner wall of a bottom portion of the sealed container.
The refrigerant compressor according to claim 1, wherein the partition member is formed in a cup shape having a through hole provided substantially coaxially with the lubricating oil suction port at the bottom.
The refrigerant compressor according to any one of claims 1 to 2, wherein a heat dissipating fin is installed outside the lubricating oil reservoir of the sealed container.
The bottom portion of the sealed container in the vicinity of the lubricating oil suction port is formed in a recessed shape, and the lower end portion of the drive shaft is disposed inside the recessed shape. The refrigerant compressor as described in any one of these.
The refrigerant compressor according to claim 4, wherein a heat radiation fin is provided outside the hollow shape at the bottom of the sealed container.
The sealed container includes support legs;
The refrigerant compressor according to any one of claims 1 to 2, wherein a heat radiating fin is provided at a distal end portion of the support leg.
The oil supply path to the lubricating oil suction port and the vane back pressure chamber of the compression mechanism portion of the vane compressor are communicated with each other through an independent connection channel. The refrigerant compressor according to item.
The refrigerant compressor according to any one of claims 1 to 7, wherein an inner wall portion of the sealed container corresponding to the oil supply path is formed in an uneven shape.
The lubricating oil relief hole for limiting the amount of the lubricating oil flowing out to a small amount is provided below a cup-shaped side surface forming the partition member. The refrigerant compressor described.
An insulated enclosure is installed around the sealed container,
The heat-insulating enclosure has at least one of the hollow shape formed at the bottom of the sealed container, the heat radiation fin provided at the hollow shape, or the heat radiation fin provided at the bottom of the sealed container. The refrigerant compressor according to any one of claims 1 to 5, wherein the refrigerant compressor is opened so as to be exposed.
The heat insulating material to be wound around the sealed container is wound only on the upper region of the sealed container, and is not wound on the lower region corresponding to the lubricating oil reservoir. The refrigerant compressor according to any one of 10.
The compression mechanism section includes a low-stage compression mechanism section that compresses the refrigerant from a low pressure to an intermediate pressure, and a high-stage compression mechanism section that compresses the refrigerant from an intermediate pressure to a high pressure.
The low-stage compression mechanism section includes a low-stage discharge muffler outer container having an injection refrigerant inlet, and a low-stage discharge muffler inner container that mixes the injected injection refrigerant and the refrigerant discharged from the low-stage compression mechanism section. Prepared,
A connection channel for introducing the mixed refrigerant into the high-stage compression mechanism,
The refrigerant compressor according to any one of claims 1 to 11, wherein the low-stage discharge muffler outer container is installed in an inner space of the lubricating oil reservoir partitioned by the partition member. .
The compression mechanism section includes a low-stage compression mechanism section that compresses the refrigerant from a low pressure to an intermediate pressure, and a high-stage compression mechanism section that compresses the refrigerant from an intermediate pressure to a high pressure.
The low-stage compression mechanism section includes an injection refrigerant inlet, and includes a low-stage discharge muffler container that mixes the injected injection refrigerant and the refrigerant discharged from the low-stage compression mechanism section,
A connecting flow path for introducing the mixed refrigerant into the high-stage compression mechanism, and a high-stage discharge muffler for discharging the refrigerant discharged from the high-stage compression mechanism to the upper space of the sealed container through a second connection flow path. A container,
The refrigerant compressor according to any one of claims 1 to 11, wherein the high-stage discharge muffler container is installed in an inner space of the lubricating oil storage section partitioned by the partition member.