GB2553711A - Refrigerant compressor and vapor-compression refrigeration cycle device comprising same - Google Patents

Refrigerant compressor and vapor-compression refrigeration cycle device comprising same Download PDF

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Publication number
GB2553711A
GB2553711A GB1716656.2A GB201716656A GB2553711A GB 2553711 A GB2553711 A GB 2553711A GB 201716656 A GB201716656 A GB 201716656A GB 2553711 A GB2553711 A GB 2553711A
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United Kingdom
Prior art keywords
vane
cylinder
passage
oilsupply
refrigerant compressor
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Granted
Application number
GB1716656.2A
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GB2553711B (en
GB201716656D0 (en
Inventor
Moroe Shogo
Yokoyama Tetsuhide
Takahashi Shinichi
Sugiura Kanichiro
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/12—Magnetic properties

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

A second compression mechanism (20) in a refrigerant compressor (100) has a cylinder deactivation mechanism (50) that switches between compression operation and cylinder deactivation operation. The cylinder deactivation mechanism (50) comprises a magnetic body (53) that causes an attractive magnetic force to be generated that attracts a second vane (24) in a direction away from a second piston (23). The magnetic body (53) is provided facing a vane rear chamber (25) and comprises a surface (53a) facing a rear end section (24b) of the second vane (24). Oil supply flow paths (55a, 55b) that supply lubricating oil stored inside a sealed container (3) to the vane rear chamber (25) are provided in the second compression mechanism (20), said oil being supplied along an upper surface (53b) and a lower surface (53c) of the magnetic body (53) that have a different orientation to the surface (53a) of the magnetic body. Part of an inner wall surface of the oil supply flow paths (55a, 55b) comprise the upper surface (53b) and the lower surface (53c).

Description

(56) Documents Cited:
WO 2012/086779 A1 JP 2010163926 A US 20080056923 A1 (58) Field of Search: INT CL F04C (71) Applicant(s):
Mitsubishi Electric Corporation (Incorporated in Japan)
2-3 Marunouchi 2-chome, Chiyoda-ku, Tokyo, Japan (72) Inventor(s):
Shogo Moroe Tetsuhide Yokoyama Shinichi Takahashi Kanichiro Sugiura (74) Agent and/or Address for Service:
Mewburn Ellis LLP
City Tower, 40 Basinghall Street, LONDON,
Greater London, EC2V 5DE, United Kingdom (54) Title of the Invention: Refrigerant compressor and vapor-compression refrigeration cycle device comprising same
Abstract Title: Refrigerant compressor and vapor-compression refrigeration cycle device comprising same (57) A second compression mechanism (20) in a refrigerant compressor (100) has a cylinder deactivation mechanism (50) that switches between compression operation and cylinder deactivation operation. The cylinder deactivation mechanism (50) comprises a magnetic body (53) that causes an attractive magnetic force to be generated that attracts a second vane (24) in a direction away from a second piston (23). The magnetic body (53) is provided facing a vane rear chamber (25) and comprises a surface (53a) facing a rear end section (24b) of the second vane (24). Oil supply flow paths (55a, 55b) that supply lubricating oil stored inside a sealed container (3) to the vane rear chamber (25) are provided in the second compression mechanism (20), said oil being supplied along an upper surface (53b) and a lower surface (53c) of the magnetic body (53) that have a different orientation to the surface (53a) of the magnetic body. Part of an inner wall surface of the oil supply flow paths (55a, 55b) comprise the upper surface (53b) and the lower surface (53c).
[04]
Figure GB2553711A_D0001
>
1/9
FIG. 1
100
Figure GB2553711A_D0002
2/9
Figure GB2553711A_D0003
Figure GB2553711A_D0004
Sd
FIG. 4
29 25
3/9
Figure GB2553711A_D0005
>53
FIG. 5
Figure GB2553711A_D0006
4/9
FIG. 6 r lb.
Figure GB2553711A_D0007
( 56a 55 a 55a1
I 53b
54a 56a 55 a 55a1 / v I
Figure GB2553711A_D0008
5/θ
F}/^· Q
IV3. Q
Figure GB2553711A_D0009
6/9
FIG. 9
Figure GB2553711A_D0010
Figure GB2553711A_D0011
\ 54a
FIG. 11
7/9
Figure GB2553711A_D0012
25
FIG 12
Figure GB2553711A_D0013
8/9
FIG, 13
100
Figure GB2553711A_D0014
9/9
Figure GB2553711A_D0015
DESCRIPTION
Title of Invention
REFRIGERANT COMPRESSOR AND VAPOR COMPRESSION REFRIGERATION
CYCLE APPARATUS INCLUDING THE SAME
Technical Field [0001]
The present invention relates to a refrigerant compressor configured to compress refrigerant and a vapor compression refrigeration cycle apparatus including the same.
Background Art [0002]
A conventional heat pump apparatus such as an air-conditioning apparatus and a water heater typically includes a vapor compression refrigeration cycle apparatus using a refrigerant compressor. Specifically, the heat pump apparatus has a refrigeration cycle in which the refrigerant compressor, a radiator, an expansion mechanism, and an evaporator are connected with each other through pipes. With this configuration, the heat pump apparatus is configured to execute an operation corresponding to its usage (for example, air conditioning usage or water heating usage).
[0003]
In recent years, energy saving regulations on air conditioning apparatuses have been tightened in a number of countries, and operation standards are being changed to those substantially under actual loads. In Japan, indication of efficiency improvement was used to be in an average COP in cooling and heating, but has changed to indication in an annual performance factor (APF) since 2011. The energy saving standards for an air-conditioning apparatus and a water heater are expected to be changed to new standards closer to actual loads. For example, when a rated heating capacity needed at start-up of an air-conditioning apparatus is assumed to be 100%, a constantly needed heating capacity is 10% to 50% approximately, and the efficiency in this low-load region affects the APF more largely than the rated capacity.
[0004]
For this reason, on-off control has been used for many years to adjust a cooling-heating capacity. This on-off control, however, has problems such as increase in temperature adjustment fluctuation and vibration noise, and impaired energy saving performance. Thus, in recent years, inverter control, in which the rotation frequency of an electric motor configured to drive the refrigerant compressor is variable, has been increasingly used to improve the energy saving performance, for example.
[0005]
An air-conditioning apparatus needs a rated capacity at a certain level due to recent requirement for reduction of a start-up time and operation in a severer environment (at low temperature or high temperature). On the other hand, the constantly needed capacity decreases as thermal insulation at home is highly improved, which results in a wider operational capacity range. Consequently, the rotation frequency of the refrigerant compressor is varied in a wider range through an inverter, and a highly efficient operation of the refrigerant compressor tends to be required in a wider rotation frequency range. Thus, in the conventional airconditioning apparatus, it is difficult to maintain, under a low-load capacity condition, the highly efficient operation of the refrigerant compressor by continuously operating the refrigerant compressor at a reduced rotation frequency.
[0006]
For this reason, a refrigerant compressor including a unit (mechanical capacity control unit) capable of mechanically changing an excluded volume has become popular again. For example, Patent Literatures 1 and 2 each disclose a refrigerant compressor including two of a first compression mechanism unit and a second compression mechanism unit. Under a high load, a compression operation is performed at both compression mechanism units. Under a low load, a compression operation is performed at one of the compression mechanism units while a cylinder resting operation (non-compression operation) is performed at the other compression mechanism unit, thereby halving the flow rate of refrigerant circulation flow and thus achieving a halved capacity.
[0007]
In the refrigerant compressor disclosed in Patent Literature 1, a vane of each compression mechanism unit is reciprocatingly housed in a vane groove, and has a rear end part positioned in a vane back chamber communicated with the vane groove. The vane back chamber is communicated with an internal space of a sealed container to receive the pressure (high pressure) in the internal space, and this high pressure acts on the rear end part of the vane.
[0008]
In a compression operation state, low-pressure refrigerant is introduced into a cylinder chamber of each compression mechanism unit to apply low pressure or middle pressure on a front end part of the vane and apply high pressure on the rear end part of the vane as described above. Consequently, a pressure difference is generated between the front and rear end parts of the vane. In the compression operation state, the front end part of the vane is pressed to contact a piston because of this pressure difference, and a normal compression operation is performed.
[0009]
In a cylinder resting operation state, high-pressure refrigerant is introduced into the cylinder chamber by a switching mechanism to apply high pressure on the front and rear end parts of the vane and thus cancel the pressure difference between the front and rear end parts of the vane. When the pressure difference is cancelled, the front end part of the vane is separated from an outer peripheral surface of the piston. Consequently, no compression effect is generated in the cylinder resting operation state.
[0010]
In the refrigerant compressor disclosed in Patent Literature 2, similarly to that in
Patent Literature 1, in the compression operation, suction pressure (low pressure) acts on the front end part of the vane, and discharge pressure (high pressure) acts on the rear end part of the vane. In the technology of Patent Literature 2, the vane back chamber includes a permanent magnet that generates an attractive magnetic force attracting the vane in a direction in which the vane is caused to separate from the piston. Thus, in the technology of Patent Literature 2, a pressing force acts on the vane in a direction in which the vane is caused to contact the piston, and simultaneously, the attractive magnetic force acts on the vane in the direction in which the vane is caused to separate from the piston. When the pressing force is smaller than the attractive magnetic force, the vane becomes separated from the piston and the cylinder resting operation is performed. When the pressing force is larger than the attractive magnetic force, the vane contacts the piston and the compression operation is performed.
[0011]
The refrigerant compressors disclosed in Patent Literatures 1 and 2 described above can both halve the refrigerant circulation flow rate by performing the cylinder resting operation (non-compression operation) at one ofthe compression mechanism units, and thus can operate with the rotation frequency of an electric motor being maintained under a low load. The refrigerant compressor can thus obtain improved compressor efficiency.
Citation List
Patent Literature [0012]
Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2005-171847
Patent Literature 2: International Publication No. WO 2014/175429 Summary of Invention Technical Problem [0013]
The refrigerant compressor disclosed in Patent Literature 1 includes a mechanical capacity control unit employing a cylinder resting operation scheme to improve an efficiency decrease under a low-load condition. The vane back chamber of the refrigerant compressor includes, as the mechanical capacity control unit, a permanent magnet that holds the vane by attraction during the cylinder resting operation. The vane back chamber is communicated with an oil reservoir inside the sealed container to apply high pressure on the rear end part of the vane. With this configuration, any metal pieces generated at each sliding part inside the sealed container and mixed into lubricating oil are likely to be attracted by the permanent magnet provided to the vane back chamber and collected around the vane. Thus, this refrigerant compressor has a problem with decrease in the reliability of sliding parts of components such as the vane.
[0014]
In the refrigerant compressor disclosed in Patent Literature 2, the attractive magnetic force generated by the permanent magnet and acting on the vane needs to be controlled. However, when any metal piece in lubricating oil adheres to a surface of the permanent magnet or a yoke, variation occurs in the attractive magnetic force acting on the vane, which causes such a problem with difficulty in reliably switching the compression operation and the cylinder resting operation.
[0015]
The present invention is intended to solve the above-described problems by providing a refrigerant compressor capable of achieving improved reliability of a sliding part and reliably switching a compression operation and a cylinder resting operation, and a vapor compression refrigeration cycle apparatus including the same. Solution to Problem [0016]
A refrigerant compressor according to an embodiment of the present invention includes a sealed container storing lubricating oil, and a plurality of compression mechanisms housed in the sealed container. The compression mechanisms each include a cylinder including a cylinder chamber, a piston configured to eccentrically rotate in the cylinder chamber, a vane that includes a front end part configured to contact the piston and is configured to divide the cylinder chamber into a plurality of spaces, a vane groove formed in the cylinder and reciprocatingly housing the vane, and a vane back chamber formed on an outer peripheral side of the vane groove in the cylinder and housing a rear end part of the vane. At least one of the compression mechanisms includes a cylinder resting mechanism configured to switch a compression operation in which refrigerant is compressed with the front end part of the vane being in contact with the piston and a cylinder resting operation in which refrigerant is not compressed with the front end part of the vane being separated from the piston. The cylinder resting mechanism includes a magnetic body that generates an attractive magnetic force attracting the vane in a direction separating from the piston. The magnetic body includes a first surface facing the vane back chamber and opposing to the rear end part of the vane. The at least one of the compression mechanisms includes an oilsupply passage through which the lubricating oil stored in the sealed container is supplied to the vane back chamber along a second surface of the magnetic body, oriented differently from the first surface. The second surface serves as a part of an internal wall surface of the oilsupply passage.
[0017]
A vapor compression refrigeration cycle apparatus according to an embodiment of the present invention includes the refrigerant compressor according to the above-described embodiment of the present invention, a radiator configured to radiate heat of refrigerant compressed by the refrigerant compressor, an expansion mechanism configured to expand refrigerant flowing out of the radiator, and an evaporator configured to allow refrigerant flowing out of the expansion mechanism to receive heat.
Advantageous Effects of Invention [0018]
According to an embodiment of the present invention, any metal pieces mixed in the lubricating oil can be prevented from entering into the vane back chamber, thereby improving the reliability of a sliding part and achieving reliable switching of the compression operation and the cylinder resting operation.
Brief Description of Drawings [0019] [Fig. 1] Fig. 1 is a schematic longitudinal sectional view illustrating the configuration of a refrigerant compressor 100 according to Embodiment 1 of the present invention.
[Fig. 2] Fig. 2 is a schematic transverse sectional view illustrating the configuration of a first compression mechanism 10 of the refrigerant compressor 100 according to Embodiment 1 ofthe present invention.
[Fig. 3] Fig. 3 is a schematic transverse sectional view illustrating the configuration of a second compression mechanism 20 of the refrigerant compressor 100 according to Embodiment 1 ofthe present invention.
[Fig. 4] Fig. 4 is a schematic longitudinal sectional view of the configuration of the second compression mechanism 20 ofthe refrigerant compressor 100 according to Embodiment 1 ofthe present invention, illustrating part IV in Fig. 1 in an enlarged manner.
[Fig. 5] Fig. 5 is a schematic side view illustrating the configuration of the second compression mechanism 20 ofthe refrigerant compressor 100 according to Embodiment 1 of the present invention, when viewed along an extended direction of a vane groove 29.
[Fig. 6] Fig. 6 is a schematic longitudinal sectional view illustrating a modification ofthe configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to Embodiment 1 ofthe present invention.
[Fig. 7] Fig. 7 is a schematic longitudinal sectional view illustrating the configuration ofthe second compression mechanism 20 of the refrigerant compressor 100 according to Embodiment 2 of the present invention.
[Fig. 8] Fig. 8 is a schematic top view illustrating the configuration ofthe second compression mechanism 20 of the refrigerant compressor 100 according to Embodiment 2 of the present invention.
[Fig. 9] Fig. 9 is a schematic side view illustrating the configuration of the second compression mechanism 20 ofthe refrigerant compressor 100 according to
Embodiment 3 of the present invention, when viewed along the extended direction of the vane groove 29.
[Fig. 10] Fig. 10 is a schematic transverse sectional view illustrating a section along X-X in Fig. 9.
[Fig. 11] Fig. 11 is a schematic transverse sectional view illustrating the configuration ofthe second compression mechanism 20 of the refrigerant compressor 100 according to Embodiment 4 of the present invention.
[Fig. 12] Fig. 12 is a schematic longitudinal sectional view illustrating the configuration ofthe second compression mechanism 20 of the refrigerant compressor 100 according to Embodiment 5 of the present invention.
[Fig. 13] Fig. 13 is a schematic longitudinal sectional view illustrating the configuration of the refrigerant compressor 100 according to Embodiment 6 of the present invention.
[Fig. 14] Fig. 14 is a refrigerant circuit diagram illustrating the configuration of a vapor compression refrigeration cycle apparatus 500 according to Embodiment 7 of the present invention.
Description of Embodiments [0020]
Examples of a refrigerant compressor and a vapor compression refrigeration cycle apparatus according to the present invention will be described below with reference to the accompanying drawings. In the drawings described below, relations among the sizes of components are different from those in reality in some cases. In addition, three-dimensional positional relations among discharge ports and cylinder suction passages are not necessarily maintained between a longitudinal sectional view and a transverse sectional view.
[0021]
Embodiment 1
The following describes a refrigerant compressor according to Embodiment 1 of the present invention. Fig. 1 is a schematic longitudinal sectional view illustrating the configuration of a refrigerant compressor 100 according to the present embodiment. Fig. 2 is a schematic transverse sectional view illustrating the configuration of a first compression mechanism 10 of the refrigerant compressor 100 according to the present embodiment. Fig. 3 is a schematic transverse sectional view illustrating the configuration of a second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment. In the present embodiment, the refrigerant compressor 100 is, for example, a vertical rotary compressor. In the refrigerant compressor 100 illustrated in Figs. 1 to 3, the first compression mechanism 10 is in a compression operation state in which refrigerant is compressed, and the second compression mechanism 20 is in a non-compression operation state (cylinder resting operation state) in which refrigerant is not compressed.
[0022]
The refrigerant compressor 100 serves as a component of a refrigeration cycle provided in a heat pump apparatus such as an air-conditioning apparatus and a water heater. The refrigerant compressor 100 has functions of sucking gas fluid, compressing the fluid, and discharging the fluid in a high-temperature and highpressure state.
[0023]
The refrigerant compressor 100 according to the present embodiment includes, in an internal space 7 of a sealed containers, a compression mechanism 99 including the first compression mechanism 10 and the second compression mechanism 20, and an electric motor 8 configured to drive the first compression mechanism 10 and the second compression mechanism 20 through a drive shaft 5.
[0024]
The sealed container 3 is, for example, a cylindrical sealed container having blocked upper and lower end parts. A lubricating oil storage 3a (oil reservoir) storing lubricating oil for lubricating the compression mechanism 99 is provided at a bottom part of the sealed container 3. In the state illustrated in Fig. 1, the lubricating oil has an oil level positioned higher than both of the first compression mechanism 10 and the second compression mechanism 20. A compressor discharge pipe 2 is provided at an upper part of the sealed container 3 and communicated with the internal space 7 of the sealed container 3.
[0025]
The electric motor 8 includes a stator 8b and a rotor 8a. The electric motor 8 drives at a variable rotation frequency by, for example, inverter control. The stator 8b has a substantially cylindrical shape. The stator 8b has an outer periphery fixed to an inner periphery of the sealed container 3 by, for example, shrink fitting. A coil is wound around the stator 8b and supplied with electrical power from an external power source. The rotor 8a has a substantially cylindrical shape. The rotor 8a is disposed on an inner peripheral side of the stator 8b and separated from an inner peripheral surface of the stator 8b by a predetermined interval. The drive shaft 5 is fixed to the rotor 8a. The drive shaft 5 connects the electric motor 8 and the compression mechanism 99. When the electric motor 8 rotates, rotational power is transferred to the compression mechanism 99 through the drive shaft 5.
[0026]
The drive shaft 5 includes a long shaft part 5a as an upper part of the drive shaft 5, a short shaft part 5b as a lower part of the drive shaft, and an eccentric pin shaft parts 5c and 5d and an intermediate shaft part 5e that are provided between the long shaft part 5a and the short shaft part 5b. The eccentric pin shaft part 5c has a central axis eccentric to central axes of the long shaft part 5a and the short shaft part 5b by a predetermined distance, and is disposed in a first cylinder chamber 12 of the first compression mechanism 10 to be described later. The eccentric pin shaft part 5d has a central axis eccentric to the central axes of the long shaft part 5a and the short shaft part 5b by a predetermined distance, and is disposed in a second cylinder chamber 22 of the second compression mechanism 20 to be described later. The eccentric pin shaft parts 5c and 5d have phases shifted by 180 degrees from each other. The eccentric pin shaft parts 5c and 5d are connected with each other through the intermediate shaft part 5e. The intermediate shaft part 5e is disposed in a through-hole of an intermediate dividing plate 4 to be described later. The long shaft part 5a of the drive shaft 5 is rotatably supported by a bearing 60a of a first support member 60. The short shaft part 5b is rotatably supported by a bearing 70a of a second support member 70. When the drive shaft 5 rotates, the eccentric pin shaft parts 5c and 5d eccentrically rotate in the first cylinder chamber 12 and the second cylinder chamber 22, respectively.
[0027]
The compression mechanism 99 includes the first compression mechanism 10, which is a rotary type, at an upper part and the second compression mechanism 20, which is a rotary type, at a lower part. The first compression mechanism 10 and the second compression mechanism 20 are disposed below the electric motor 8. The compression mechanism 99 includes the first support member 60, a first cylinder 11 included in the first compression mechanism 10, the intermediate dividing plate 4, a second cylinder 21 included in the second compression mechanism 20, and the second support member 70 that are stacked in this order from the top.
[0028]
The first compression mechanism 10 includes the first cylinder 11, a first piston 13, a first vane 14, and other components. The first cylinder 11 is a flat plate member through which a through-hole substantially cylindrical and substantially concentric with the drive shaft 5 (more specifically, the long shaft part 5a and the short shaft part 5b) penetrates in a vertical direction of the flat plate member. The first cylinder chamber 12 is formed by blocking one of end parts (in Fig. 1, an upper end part) of this through-hole with a flange part 60b of the first support member 60, and the other end part (in Fig. 1, a lower end part) with the intermediate dividing plate 4.
[0029]
The first piston 13 is provided in the first cylinder chamber 12 of the first cylinder 11. The first piston 13 has a ring shape and is slidably provided to the eccentric pin shaft part 5c of the drive shaft 5. The first cylinder 11 is provided with a vane groove 19 communicated with the first cylinder chamber 12 and extending in a radial direction of the first cylinder chamber 12. The vane groove 19 is slidably provided with the first vane 14. When a front end part 14a of the first vane 14 contacts an outer periphery of the first piston 13, the first cylinder chamber 12 is divided into a suction chamber 12a and a compression chamber 12b.
[0030]
The first cylinder 11 includes a vane back chamber 15 on an outer peripheral side of the vane groove 19, in other words, on a back side of the first vane 14. The vane back chamber 15 penetrates through the first cylinder 11 in the vertical direction. The vane back chamber 15 includes an upper opening port partially opened to the internal space 7 of the sealed container 3 (space outside the first cylinder 11). This configuration allows lubricating oil stored in the lubricating oil storage 3a to flow into the vane back chamber 15. Having flowed into the vane back chamber 15, the lubricating oil flows between the vane groove 19 and the first vane 14 to reduce a slide resistance between the vane groove 19 and the first vane 14. As described later, in the refrigerant compressor 100 according to the present embodiment, refrigerant compressed by the compression mechanism 99 is discharged into the internal space 7 of the sealed container 3. Consequently, the vane back chamber 15 has a high-pressure atmosphere same as that in the internal space 7 of the sealed container 3.
[0031]
The second compression mechanism 20 includes the second cylinder 21, a second piston 23, a second vane 24, and other components. The second cylinder 21 is a flat plate member through which a through-hole substantially cylindrical and substantially concentric with the drive shaft 5 (more specifically, the long shaft part 5a and the short shaft part 5b) penetrates in the vertical direction of the flat plate member. The second cylinder chamber 22 is formed by blocking one of end parts (in Fig. 1, an upper end part) of the through-hole with the intermediate dividing plate 4, and the other end part (in Fig. 1, a lower end part) with a flange part 70b of the second support member 70.
[0032]
The second piston 23 is provided in the second cylinder chamber 22 of the second cylinder 21. The second piston 23 has a ring shape and is slidably provided to the eccentric pin shaft part 5d of the drive shaft 5. The second cylinder 21 is provided with a vane groove 29 communicated with the second cylinder chamber 22 and extending in a radial direction of the second cylinder chamber 22. The vane groove 29 is slidably provided with the second vane 24. When a front end part 24a of the second vane 24 contacts an outer periphery of the second piston 23, the second cylinder chamber 22 is divided into a suction chamber and a compression chamber, similarly to the first cylinder chamber 12.
[0033]
The second cylinder 21 includes a vane back chamber 25 on an outer peripheral side of the vane groove 29, in other words, on a back side of the second vane 24. The vane back chamber 25 penetrates through the second cylinder 21 in the vertical direction of the second cylinder 21. The vane back chamber 25 includes upper and lower opening ports blocked by the intermediate dividing plate 4 and the flange part 70b of the second support member 70. The vane back chamber 25 is communicated with the internal space 7 ofthe sealed container 3 (space outside the second cylinder 21) through oilsupply passages 55a and 55b to be described later. Consequently, the vane back chamber 25 has a high-pressure atmosphere same as the internal space 7 of the sealed container 3. Lubricating oil stored in the lubricating oil storage 3a is allowed to flow from an outer peripheral side of the second cylinder 21 into the vane back chamber 25 through the oilsupply passages 55a and 55b. Having flowed into the vane back chamber 25, the lubricating oil flows between the vane groove 29 and the second vane 24 to reduce a slide resistance between the vane groove 29 and the second vane 24.
[0034]
The first cylinder 11 and the second cylinder 21 are connected with a suction muffler 6 for allowing gas refrigerant to flow into the first cylinder chamber 12 and the second cylinder chamber 22, respectively. Specifically, the suction muffler 6 includes a container 6b, an inflow pipe 6a through which low-pressure refrigerant is introduced from an evaporator to the container 6b, an outflow pipe 6c through which gas refrigerant from refrigerant stored in the container 6b is introduced to the first cylinder chamber 12 of the first cylinder 11, and an outflow pipe 6d through which gas refrigerant from refrigerant stored in the container 6b is introduced to the second cylinder chamber 22 of the second cylinder 21. The outflow pipe 6c of the suction muffler 6 is connected with a cylinder suction passage 17 communicated with the first cylinder chamber 12 of the first cylinder 11. The outflow pipe 6d of the suction muffler 6 is connected with a cylinder suction passage 27 communicated with the second cylinder chamber 22 of the second cylinder 21.
[0035]
The first cylinder 11 includes a discharge port 18 through which gas refrigerant compressed in the first cylinder chamber 12 is discharged. The discharge port 18 is communicated with a through-hole (not illustrated) formed at the flange part 60b of the first support member 60. This through-hole is provided with an on-off valve (not illustrated) configured to open when pressure in the first cylinder chamber 12 becomes equal to or higher than a predetermined pressure. A discharge muffler 63 is attached to the first support member 60 to cover the on-off valve (in other words, the through-hole of the flange part 60b). Similarly, the second cylinder 21 is provided with a discharge port 28 through which gas refrigerant compressed in the second cylinder chamber 22 is discharged. The discharge port 28 is communicated with a through-hole (not illustrated) formed at the flange part 70b of the second support member 70. This through-hole is provided with an on-off valve (not illustrated) configured to open when pressure in the second cylinder chamber 22 becomes equal to or higher than a predetermined pressure. A discharge muffler 73 is attached to the second support member 70 to cover the on-off valve (in other words, the through-hole of the flange part 70b).
[0036]
As described above, the first compression mechanism 10 and the second compression mechanism 20 have the same basic configuration. However, detailed configurations of the first compression mechanism 10 and the second compression mechanism 20 are different from each other as described below. In the following description, among forces acting on the first vane 14 and the second vane 24, a first force is defined to be a force applied in a direction in which the first vane 14 or the second vane 24 is caused to contact the first piston 13 or the second piston 23, respectively. In addition, among forces acting on the second vane 24, a second force is defined to be a force applied in a direction in which the second vane 24 is caused to separate from the second piston 23.
[0037]
The first cylinder chamber 12 and the second cylinder chamber 22 are both always communicated with a suction pressure space, and the vane back chambers 15 and 25 are both always communicated with a discharge pressure space. With this configuration, a suction pressure acts on the front end parts 14a and 24a of the first vane 14 and the second vane 24, respectively, and a discharge pressure acts on rear end parts 14b and 24b of the first vane 14 and the second vane 24, respectively. The first forces act on the first vane 14 and the second vane 24 due to differences between the pressures acting on the front end parts 14a and 24a and the rear end parts 14b and 24b, respectively.
[0038]
The vane back chamber 15 of the first compression mechanism 10 is provided with a compression spring 40 pressing the first vane 14 in a direction in which the first vane 14 is caused to contact the first piston 13. In other words, the first force still acts on the first vane 14 of the first compression mechanism 10 when the pressures acting on the front end part 14a and the rear end part 14b have no difference.
[0039]
The second compression mechanism 20 includes a cylinder resting mechanism 50 configured to switch a compression operation and a cylinder resting operation.
The cylinder resting mechanism 50 includes a magnetic body 53 that generates an attractive magnetic force attracting the second vane 24 in a direction separating from the second piston 23. In the present example, the magnetic body 53 includes a permanent magnet 51 and a yoke 52. The permanent magnet 51 is disposed on the back side of the second vane 24. The yoke 52 is laminated on a surface of the permanent magnet 51 on a side of the second vane 24. The permanent magnet 51 and the yoke 52 are fixed to the second cylinder 21 by, for example, magnetic force of the permanent magnet 51. The permanent magnet 51 and the yoke 52 may be held by, for example, passage formation members 54a and 54b to be described later. A surface 53a of the magnetic body 53 (in other words, a surface of the yoke 52) opposes to the rear end part 24b of the second vane 24. The surface 53a of the magnetic body 53 faces the vane back chamber 25 and serves as a part of an internal wall surface of the vane back chamber 25.
[0040]
The attractive magnetic force of the permanent magnet 51 acts on the second vane 24 as the second force in the direction separating from the second piston 23. The attractive magnetic force (second force) acting on the second vane 24 increases as the second vane 24 is positioned closer to the permanent magnet 51. In the present example, the magnetic body 53 includes the permanent magnet 51 and the yoke 52, but may include the permanent magnet 51 only.
[0041]
The first force and the second force are always acting on the second vane 24. Thus, the second compression mechanism 20 is autonomously switched between the compression operation state and the cylinder resting operation state depending on a magnitude relation between the first force and the second force acting on the second vane 24. Specifically, when the first force is larger than the second force, the front end part 24a of the second vane 24 contacts the second piston 23, and thus the second compression mechanism 20 becomes the compression operation state.
When the second force is larger than the first force, the second vane 24 becomes separated from the second piston 23 and attracted onto the surface 53a of the magnetic body 53. Consequently, no compression chamber is formed in the second cylinder chamber 22, and thus the second compression mechanism 20 becomes the cylinder resting operation state. As the second vane 24 moves closer to the permanent magnet 51 once the second vane 24 is separated from the second piston 23, the second force acting on the second vane 24 increases.
[0042]
The first force needs to be larger than the second force to achieve switching from the cylinder resting operation state to the compression operation state.
However, the second force when the second vane 24 is attracted onto the surface 53a of the magnetic body 53 is larger than the second force when the second vane 24 is separated from the second piston 23. Thus, the first force necessary for switching from the cylinder resting operation state to the compression operation state is larger than the first force when the compression operation state is switched to the cylinder resting operation state.
[0043]
The following describes an operation of compressing refrigerant at both of the first compression mechanism 10 and the second compression mechanism 20. This operation is same as an operation of a normal rotary compressor in which no compression mechanism becomes the cylinder resting operation state. Detailed description of the operation will be made below.
[0044]
When supplied with electrical power, the electric motor 8 rotates the drive shaft 5 anticlockwise (in directions indicated by thick arrows in Figs. 2 and 3) when viewed from above. When the drive shaft 5 rotates, the eccentric pin shaft part 5c eccentrically rotates in the first cylinder chamber 12 and the eccentric pin shaft part 5d eccentrically rotates in the second cylinder chamber 22. The eccentric pin shaft parts 5c and 5d eccentrically rotate with their phases different from each other by 180 degrees.
[0045]
As the eccentric pin shaft part 5c eccentrically rotates, the first piston 13 eccentrically rotates in the first cylinder chamber 12 to compress low-pressure gas refrigerant sucked into the first cylinder chamber 12 from the outflow pipe 6c of the suction muffler 6 through the cylinder suction passage 17. Similarly, as the eccentric pin shaft part 5d eccentrically rotates, the second piston 23 eccentrically rotates in the second cylinder chamber 22 to compress low-pressure gas refrigerant sucked into the second cylinder chamber 22 from the outflow pipe 6d of the suction muffler 6 through the cylinder suction passage 27.
[0046]
Once compressed to a predetermined the pressure in the first cylinder chamber 12, the gas refrigerant is discharged into the discharge muffler 63 through the discharge port 18, and then discharged from the discharge port of the discharge muffler 63 into the internal space 7 of the sealed container 3. Once compressed to a predetermined the pressure in the second cylinder chamber 22, the gas refrigerant is discharged into the discharge muffler 73 through the discharge port 28, and then discharged from the discharge port of the discharge muffler 73 into the internal space 7 of the sealed container 3. Then, the high-pressure gas refrigerant discharged into the internal space 7 of the sealed container 3 is discharged to the outside of the sealed container 3 through the compressor discharge pipe 2.
[0047]
To compress refrigerant at the first compression mechanism 10 and the second compression mechanism 20, the above-described refrigerant compression operation is repeated at the first compression mechanism 10 and the second compression mechanism 20.
[0048]
The following describes an operation of the second compression mechanism 20 in the cylinder resting operation state. In this operation, the first vane 14 of the first compression mechanism 10 is constantly in contact with the first piston 13, by being pressed by the compression spring 40. Consequently, the first compression mechanism 10 performs the refrigerant compression operation as described above. Thus, the following only describes an operation of the second compression mechanism 20.
[0049]
When the second compression mechanism 20 is in the compression operation state, the discharge pressure acts on the rear end part 24b of the second vane 24 through lubricating oil. In this case, a pressing force (first force) acting on the second vane 24 due to a difference between pressures acting on the front end part 24a and the rear end part 24b of the second vane 24 is larger than the attractive magnetic force of the permanent magnet 51 (second force). Consequently, the front end part 24a of the second vane 24 is pressed against an outer peripheral surface of the second piston 23. Thus, refrigerant is compressed at the second compression mechanism 20 as the drive shaft 5 rotates.
[0050]
However, right after the refrigerant compressor 100 starts operating or when a load on the refrigerant compressor 100 is low, pressure in the internal space 7 of the sealed container 3 is relatively low. Thus, the attractive magnetic force of the permanent magnet 51 (second force) exceeds the pressing force (first force) generated by the difference between pressures acting on the front end part 24a and the rear end part 24b of the second vane 24. Consequently, the second vane 24 becomes separated from the outer peripheral surface of the second piston 23, and the second compression mechanism 20 becomes the cylinder resting operation state. [0051]
Then, as the front end part 24a of the second vane 24 becomes separated from the outer peripheral surface of the second piston 23 and the rear end part 24b of the second vane 24 moves closer to the permanent magnet 51, the attractive magnetic force on the second vane 24 increases. Consequently, the second vane 24 further moves in the direction separating from the second piston 23, and the rear end part 24b of the second vane 24 becomes in contact with the yoke 52 and held by attraction.
[0052]
The following describes an operation to cancel the cylinder resting operation state of the second compression mechanism 20. As the pressure (discharge pressure) in the internal space 7 of the sealed container 3 increases in the cylinder resting operation state, the pressing force (first force) acting on the second vane 24 due to the pressure difference between the front end part 24a and the rear end part 24b of the second vane 24 becomes larger than the attractive magnetic force of the permanent magnet 51 (second force). In this state, the second vane 24 becomes separated from the yoke 52, and consequently the attraction holding of the second vane 24 is canceled.
[0053]
Then, as the rear end part 24b of the second vane 24 becomes separated from the permanent magnet 51, the attractive magnetic force on the second vane 24 decreases, and thus the difference between the first force and the second force increases. Consequently, the second vane 24 moves further closer to the second piston 23, so that the front end part 24a of the second vane 24 is pressed against the outer peripheral surface of the second piston 23 and the second compression mechanism 20 starts the refrigerant compression operation.
[0054]
As described above, the vane back chamber 25 is provided with the permanent magnet 51 and the yoke 52 to switch the operation state of the second compression mechanism 20. However, when the refrigerant compressor 100 is operating, metal pieces in sizes of several pm to several hundred pm are generated due to sliding of the vanes, the pistons, the drive shaft, and the other components inside the compression mechanism 99. The generated metal pieces flow into the internal space 7 of the sealed container 3 together with compressed refrigerant and lubricating oil. The metal pieces in the internal space 7 flow into the vane back chamber 25 together with lubricating oil, and are likely to be attracted onto the magnetic body 53 by the attractive magnetic force. For example, any metal piece adhering to the surface 53a of the magnetic body 53 causes variation in the attractive magnetic force acting on the second vane 24. This variation changes a pressure condition under which the operation state ofthe second compression mechanism 20 is switched, which potentially makes it difficult to reliably control the operation state of the second compression mechanism 20. This problem is solved by the present embodiment configured as described below.
[0055]
Fig. 4 is a schematic longitudinal sectional view of the configuration of the second compression mechanism 20, illustrating part IV (part enclosed by a dashed line) in Fig. 1 in an enlarged manner. Fig. 5 is a schematic side view illustrating the configuration of the second compression mechanism 20 when viewed along the extended direction of the vane groove 29. As illustrated in Figs. 4 and 5, the passage formation members 54a and 54b are provided at upper and lower ends of the vane back chamber 25 of the second cylinder 21 in the axial direction. The passage formation members 54a and 54b form the oilsupply passages 55a and 55b, respectively, communicated with the internal space 7 and the vane back chamber 25. The passage formation members 54a and 54b, in other words, the oilsupply passages 55a and 55b are formed substantially vertically symmetric with each other. Lubricating oil in the lubricating oil storage 3a is supplied from the outer peripheral side of the second cylinder 21 to the vane back chamber 25 through the oilsupply passages 55a and 55b. Having supplied to the vane back chamber 25, the lubricating oil flows into, for example, a sliding part between the second vane 24 and the vane groove 29. Fig. 4 illustrates an exemplary lubricating oil flow with an arrow. [0056]
The passage formation members 54a and 54b are made of a non-magnetic material. The passage formation members 54a and 54b are attached to the second cylinder 21 with the second cylinder 21 interposed between the passage formation members 54a and 54b in the axial direction. The passage formation members 54a and 54b may be fixed to upper and lower surfaces, respectively, of the second cylinder 21, or may be fixed to outer peripheral surfaces of the intermediate dividing plate 4 and the second support member 70, respectively.
[0057]
The oilsupply passage 55a extends in a direction parallel to an upper surface 53b of the magnetic body 53 and along a radial direction of the second cylinder 21.
An inflow port 55a1 of the oilsupply passage 55a is provided at a rear end part (outer peripheral end part) of the passage formation member 54a, opposing to an inner peripheral surface of the sealed container 3. The upper surface 53b of the magnetic body 53 serves as a part of the internal wall surface that defines the oilsupply passage 55a. Similarly, the oilsupply passage 55b extends in a direction parallel to a lower surface 53c of the magnetic body 53 and along the radial direction of the second cylinder 21. An inflow port 55b1 of the oilsupply passage 55b is provided at a rear end part (outer peripheral end part) of the passage formation member 54b, opposing to the inner peripheral surface of the sealed container 3. The lower surface 53c of the magnetic body 53 serves as a part of the internal wall surface that defines the oilsupply passage 55b. The upper surface 53b and the lower surface 53c of the magnetic body 53 are oriented differently from the surface 53a of the magnetic body 53. The surface 53a is disposed downstream of the upper surface 53b in the flow of lubricating oil through the oilsupply passage 55a. The surface 53a is disposed downstream of the lower surface 53c in the flow of lubricating oil through the oilsupply passage 55b.
[0058]
A width W1 of the oilsupply passage 55a in the direction along the upper surface 53b is restricted to be equal to or smaller than a width W3 of the magnetic body 53 (W1 < W3). A height H1 of the oilsupply passage 55a in a direction orthogonal to the upper surface 53b is set to, for example, 10 mm or smaller so that the oilsupply passage 55a is entirely included in the range of a magnetic field generated by the permanent magnet 51 and having a predetermined strength in the side view illustrated in Fig. 5. Consequently, when metal pieces 80 are mixed in lubricating oil flowing through the oilsupply passage 55a, the metal pieces 80 all pass inside the range of the magnetic field generated by the permanent magnet 51. Thus, before entering into the vane back chamber 25, the metal pieces 80 in the lubricating oil are captured by the magnetic force of the permanent magnet 51 and attracted onto the upper surface 53b of the magnetic body 53. As a result, the metal pieces 80 can be prevented from entering into the vane back chamber 25 or the sliding part through the oilsupply passage 55a. In addition, as the metal pieces 80 in the lubricating oil can be prevented from entering into the vane back chamber 25, the metal pieces 80 can be prevented from being attracted onto the surface 53a of the magnetic body 53. [0059]
For the same reason, a width W2 of the oilsupply passage 55b in the direction along the lower surface 53c is restricted to be equal to or smaller than the width W3 of the magnetic body 53 (W2 < W3). A height H2 of the oilsupply passage 55b in a direction orthogonal to the lower surface 53c is set to, for example, 10 mm or smaller. Consequently, the metal pieces 80 can be prevented from entering into the vane back chamber 25 or the sliding part through the oilsupply passage 55b, and also can be prevented from being attracted onto the surface 53a of the magnetic body 53.
[0060]
Mesh members 56a and 56b made of a metallic material such as a ferrous material are provided downstream of the upper surface 53b in the oilsupply passage 55a and downstream of the lower surface 53c in the oilsupply passage 55b, respectively. In the present example, the mesh members 56a and 56b are disposed close to boundaries between the oilsupply passages 55a and 55b and the vane back chamber 25, respectively. The mesh members 56a and 56b allow lubricating oil to pass through but prevent the metal pieces 80 from passing through. In the present example, the mesh member 56a is fixed by being sandwiched between the second cylinder 21 and the intermediate dividing plate 4, and the mesh member 56b is fixed by being sandwiched between the second cylinder 21 the second support member 70. When the mesh members 56a and 56b are provided, any small metal piece 80 that cannot be captured by the magnetic force of the permanent magnet 51 can be captured by the mesh members 56a and 56b.
[0061]
The mesh members 56a and 56b may be disposed in contact with the magnetic body 53. In this case, the mesh members 56a and 56b become magnetized to attract the metal pieces 80, thereby enhancing the effect of capturing the metal pieces 80. To actively magnetize the mesh members 56a and 56b, the mesh members 56a and 56b are made of, for example, S45C or S25C.
[0062]
Fig. 6 is a schematic longitudinal sectional view illustrating a modification of the configuration ofthe second compression mechanism 20 of the refrigerant compressor
100 according to the present embodiment. In the present modification, the mesh members 56a and 56b are rolled up and inserted into the oilsupply passages 55a and
55b, respectively. Then, the mesh members 56a and 56b are fixed to predetermined positions inside the oilsupply passages 55a and 55b by restoring forces back to their original shapes.
[0063]
As described above, in the present embodiment, the upper surface 53b and the lower surface 53c of the magnetic body 53 attracting the second vane 24, which are oriented differently from the surface 53a, serve as parts of the internal wall surfaces of the oilsupply passages 55a and 55b, respectively. With this configuration, the metal pieces 80 mixed in lubricating oil flowing through the oilsupply passages 55a and 55b can be captured at the upper surface 53b and the lower surface 53c by the magnetic force of the magnetic body 53 before flowing into the vane back chamber 25. Consequently, the metal pieces 80 can be prevented from entering into the sliding part with a simple configuration, thereby achieving an improved reliability of the sliding part. In the present embodiment, as the metal pieces 80 can be captured before reaching the surface 53a of the magnetic body 53, variation in the attractive magnetic force acting on the second vane 24 can be prevented, thereby achieving reliable switching of the compression operation and the cylinder resting operation. In the present embodiment, the oilsupply passages 55a and 55b have sizes small enough to receive effective application of the magnetic force of the magnetic body 53, thereby enhancing the effect of capturing the metal pieces 80.
[0064]
In the present embodiment, the mesh members 56a and 56b are disposed downstream of the upper surface 53b and the lower surface 53c, respectively, of the magnetic body 53 in the flow of lubricating oil through the oilsupply passages 55a and 55b. With this configuration, the mesh members 56a and 56b remove only the metal pieces 80 that cannot be removed at the upper surface 53b and the lower surface 53c. Thus, clogging of the mesh members 56a and 56b can be reduced to achieve longer lifetimes of the mesh members 56a and 56b.
[0065]
In the present embodiment, as the vane back chamber 25 and the lubricating oil storage 3a are always communicated with each other through the oilsupply passages 55a and 55b, a sufficient amount of lubricating oil can be applied to the vane back chamber 25.
[0066]
Embodiment 2
The following describes a refrigerant compressor according to Embodiment 2 of the present invention. In Embodiment 1 described above, the oilsupply passages 55a and 55b extend in parallel to the upper surface 53b and the lower surface 53c, respectively, of the magnetic body 53. When the oilsupply passages 55a and 55b are configured as described below, the metal pieces 80 can be more reliably prevented from entering into the vane back chamber 25. In the following, any configuration not described in the present embodiment is identical to that in Embodiment 1, and any identical function or component is denoted by an identical reference sign.
[0067]
Fig. 7 is a schematic longitudinal sectional view illustrating the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment. Fig. 8 is a schematic top view illustrating the configuration of the second compression mechanism 20. As illustrated in Figs. 7 and 8, the present embodiment differs from Embodiment 1 at least in that the inflow port 55a1 of the oilsupply passage 55a is formed on an upper surface of the passage formation member 54a, and the inflow port 55b1 of the oilsupply passage 55b is formed on a lower surface of the passage formation member 54b.
[0068]
In the present embodiment, a part of the oilsupply passage 55a close to the inflow port 55a1 extends orthogonally to the upper surface 53b of the magnetic body 53. The oilsupply passage 55a extends to the upper surface 53b and bends substantially at right angle at the upper surface 53b. In other words, the upper surface 53b of the magnetic body 53 serves as an outside part of the internal wall surface of the oilsupply passage 55a at the bent part. Similarly, a part of the oilsupply passage 55b close to the inflow port 55b1 extends orthogonally to the lower surface 53c of the magnetic body 53. The oilsupply passage 55b extends to the lower surface 53c and bends substantially at right angle at the lower surface 53c. In other words, the lower surface 53c of the magnetic body 53 serves as an outside part of the internal wall surface of the oilsupply passage 55b at the bent part.
[0069]
Having flowed into the oilsupply passage 55a through the inflow port 55a1, lubricating oil first flows toward the upper surface 53b of the magnetic body 53, inertial ly collides with the upper surface 53b of the magnetic body 53 at the bent part of the oilsupply passage 55a, and then flows into the vane back chamber 25.
Similarly, having flowed into the oilsupply passage 55b through the inflow port 55b1, lubricating oil first flows toward the lower surface 53c of the magnetic body 53, inertial ly collides with the lower surface 53c of the magnetic body 53 at the bent part of the oilsupply passage 55b, and then flows into the vane back chamber 25.
[0070]
Consequently, before flowing into the vane back chamber 25, the metal pieces 80 mixed in the lubricating oil pass close to the upper surface 53b or the lower surface 53c where the permanent magnet 51 generates a stronger magnetic field.
As a result, the metal pieces 80 in the lubricating oil can be more reliably attracted onto the upper surface 53b or the lower surface 53c. Thus, the present embodiment can obtain an enhanced effect of removing the metal pieces 80 as compared to that of Embodiment 1.
[0071]
Embodiment 3
The following describes a refrigerant compressor according to Embodiment 3 of the present invention. In Embodiment 1 described above, the oilsupply passages 55a and 55b extend in parallel to the upper surface 53b and the lower surface 53c, respectively, of the magnetic body 53. The metal pieces 80 can be prevented from entering into the vane back chamber 25 also when the oilsupply passages are configured as described below. In the following, any configuration not described in the present embodiment is identical to that in Embodiment 1, and any identical function or component is denoted by an identical reference sign.
[0072]
Fig. 9 is a schematic side view illustrating the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment, when viewed along the extended direction of the vane groove 29. Fig. 10 is a schematic transverse sectional view illustrating a section along X-X in Fig. 9. As illustrated in Figs. 9 and 10, in the present embodiment, at least a part of oilsupply passages 55c and 55d is formed in the second cylinder 21.
[0073]
The oilsupply passage 55c extends in a direction parallel to a left side surface 53d (side surface on the right side in Fig. 10) of the magnetic body 53 and substantially along the radial direction of the second cylinder 21. The oilsupply passage 55d extends in a direction parallel to a right side surface 53e (side surface on the left side in Fig. 10) of the magnetic body 53 and substantially along the radial direction of the second cylinder 21. Parts of the oilsupply passages 55c and 55d each have a bottomed groove shape extending from an upper surface of the second cylinder 21. The oilsupply passage 55c includes an inflow port 55c1 provided upward at an end part of the oilsupply passage 55c positioned on an outer peripheral part of the second cylinder 21. The oilsupply passage 55d includes an inflow port 55d1 provided upward at an end part of the oilsupply passage 55d positioned on the outer peripheral part of the second cylinder 21. The passage formation member 54a blocks a part of an upper part of the oilsupply passage 55c other than the inflow port 55c1, and a part of the oilsupply passage 55d other than the inflow port 55d1, as well as an upper end part of the vane back chamber 25. The vane back chamber 25 has a lower end part blocked by the passage formation member 54b.
[0074]
The left side surface 53d of the magnetic body 53 serves as a part of an internal wall surface of the oilsupply passage 55c. The surface 53a of the magnetic body 53 is disposed downstream of the left side surface 53d in the flow of lubricating oil through the oilsupply passage 55c. The right side surface 53e of the magnetic body 53 serves as a part of an internal wall surface of the oilsupply passage 55d.
The surface 53a of the magnetic body 53 is disposed downstream of the right side surface 53e in the flow of lubricating oil through the oilsupply passage 55d.
[0075]
The oilsupply passages 55c and 55d are provided with the mesh members 56a and 56b, respectively. In the present example, the mesh members 56a and 56b are disposed downstream of the permanent magnet 51 and upstream of the yoke 52 in the oilsupply passages 55c and 55d, respectively. However, the mesh members 56a and 56b may be disposed upstream of the vane back chamber 25 and downstream of the yoke 52.
[0076]
Having flowed into the oilsupply passage 55c through the inflow port 55c1, lubricating oil flows along the left side surface 53d of the magnetic body 53, and then flows into the vane back chamber 25. Similarly, having flowed into the oilsupply passage 55d through the inflow port 55d1, lubricating oil flows along the right side surface 53e of the magnetic body 53, and then flows into the vane back chamber 25. Consequently, the metal pieces 80 mixed in the lubricating oil enter into the magnetic field of the magnetic body 53, become attracted onto the left side surface 53d or the right side surface 53e, and thus can be prevented from entering into the vane back chamber 25. As a result, the present embodiment can obtain an effect same as that of Embodiment 1. In addition, as the oilsupply passages 55c and 55d are formed in the second cylinder 21 in the present embodiment, any component for forming the oilsupply passages 55c and 55d can be omitted, thereby preventing increase in the number of components.
[0077]
Embodiment 4
The following describes a refrigerant compressor according to Embodiment 4 of the present invention. In Embodiment 3 described above, the oilsupply passages
55c and 55d extend in parallel to the left side surface 53d and the right side surface
53e, respectively, of the magnetic body 53. When the oilsupply passages are configured as described below, the metal pieces 80 can be more reliably prevented from entering into the vane back chamber 25. In the following, any configuration not described in the present embodiment is identical to that in Embodiment 1, and any identical function or component is denoted by an identical reference sign.
[0078]
Fig. 11 is a schematic transverse sectional view of the configuration of the second compression mechanism 20 ofthe refrigerant compressor 100 according to the present embodiment, illustrating a section corresponding to Fig. 10. As illustrated in Fig. 11, an oilsupply passage 55e is formed in the second cylinder 21. The oilsupply passage 55e extends in a direction orthogonal to the left side surface 53d of the magnetic body 53 (side surface on the right side in Fig. 11) and parallel to a tangential direction of the second cylinder 21. A part of the oilsupply passage 55e has, for example, a bottomed groove shape extending from the upper surface of the second cylinder 21. The oilsupply passage 55e includes an inflow port 55e1 provided upward at an end part of the oilsupply passage 55e positioned on the outer peripheral part of the second cylinder 21. The passage formation member 54a blocks a part of an upper part of the oilsupply passage 55e other than the inflow port 55e1, as well as the upper end part of the vane back chamber 25. The passage formation member 54b (not illustrated in Fig. 11) blocks a lower end part of the vane back chamber 25.
[0079]
The left side surface 53d of the magnetic body 53 serves as a part of an internal wall surface of the oilsupply passage 55e. The surface 53a of the magnetic body 53 is disposed downstream of the left side surface 53d in the flow of lubricating oil through the oilsupply passage 55e. A mesh member 56c is rolled up and provided downstream of the left side surface 53d of the magnetic body 53 in the oilsupply passage 55e.
[0080]
Having flowed into the oilsupply passage 55e through the inflow port 55e1, lubricating oil flows toward the left side surface 53d of the magnetic body 53, collides with the left side surface 53d, and then flows into the vane back chamber 25. Consequently, before flowing into the vane back chamber 25, the metal pieces 80 mixed in the lubricating oil pass close to the left side surface 53d where the permanent magnet 51 generates a stronger magnetic field. As a result, the metal pieces 80 in the lubricating oil can be more reliably attracted onto the left side surface 53d. Thus, the present embodiment can obtain an enhanced effect of removing the metal pieces 80 as compared to that of Embodiment 3.
[0081]
Embodiment 5
The following describes a refrigerant compressor according to Embodiment 5 of the present invention. In Embodiments 1 to 4 described above, the mesh members 56a to 56c are disposed downstream of the magnetic body 53 in the flow of lubricating oil. When the mesh members are disposed as described below, however, the metal pieces 80 can be still prevented from entering into the vane back chamber 25.
[0082]
Fig. 12 is a schematic longitudinal sectional view illustrating the configuration of the second compression mechanism 20 of the refrigerant compressor 100 according to the present embodiment. As illustrated in Fig. 12, the mesh members 56a and 56b according to the present embodiment are disposed upstream of the magnetic body 53 in the flow of lubricating oil through the oilsupply passages 55a and 55b.
With this configuration, the metal pieces 80 that are relatively large are captured by the mesh members 56a and 56b, and the metal pieces 80 that are relatively small are captured by the upper surface 53b and the lower surface 53c of the magnetic body 53. According to the present embodiment, too, the metal pieces 80 can be prevented from entering into the vane back chamber 25 as in Embodiments 1 to 4, thereby improving the reliability of the sliding part of the refrigerant compressor 100 and hence improving the stability of the attractive magnetic force acting on the vane.
[0083]
Embodiment 6
The following describes a refrigerant compressor according to Embodiment 6 of the present invention. In Embodiments 1 to 5 described above, the compression operation and the cylinder resting operation is switched depending on the magnitude relation between the first force and the second force acting on the second vane 24.
An effect same as those of Embodiments 1 to 5 can be obtained in switching the cylinder resting operation and the compression operation as describes below.
[0084]
Fig. 13 is a schematic longitudinal sectional view illustrating the configuration of the refrigerant compressor 100 according to the present embodiment. In the following, any configuration not described in the present embodiment is identical to that in Embodiment 1, and any identical function or component is denoted by an identical reference sign.
[0085]
As illustrated in Fig. 13, the refrigerant compressor 100 according to the present embodiment includes a pressure switching valve 150 provided to the outflow pipe 6d of the suction muffler 6, and a bypass pipe 160 connecting the compressor discharge pipe 2 and the pressure switching valve 150. The pressure switching valve 150 switches a destination to which the cylinder suction passage 27 is connected. When the pressure switching valve 150 is switched to a passage illustrated with a solid line in Fig. 13, the cylinder suction passage 27 becomes communicated with the outflow pipe 6d of the suction muffler 6. When the pressure switching valve 150 is switched to a passage illustrated with a dashed line in Fig. 13, the cylinder suction passage 27 becomes communicated with the bypass pipe 160. [0086]
When the cylinder suction passage 27 is communicated with the outflow pipe
6d of the suction muffler 6, low-pressure refrigerant is introduced to the second cylinder chamber 22 through the suction muffler 6, and thus the suction pressure acts on the front end part 24a of the second vane 24. Similarly to Embodiment 1, the discharge pressure acts on the rear end part 24b of the second vane 24. When the pressing force (first force) acting on the second vane 24 due to the pressure difference between the front end part 24a and the rear end part 24b of the second vane 24 exceeds the attractive magnetic force of the permanent magnet 51 (second force), the front end part 24a of the second vane 24 contacts the second piston 23. Thus, the operation state of the second compression mechanism 20 is autonomously switched between the cylinder resting operation and the compression operation. [0087]
When the cylinder suction passage 27 is communicated with the bypass pipe 160 by switching of the pressure switching valve 150, refrigerant at high pressure (the discharge pressure) is introduced to the second cylinder chamber 22 through the bypass pipe 160. Consequently, the discharge pressure acts on both of the front end part 24a and the rear end part 24b of the second vane 24, and the first force becomes weaker than the second force. As a result, the rear end part 24b of the second vane 24 is held by the magnetic body 53 by attraction, and thus the second compression mechanism 20 becomes the cylinder resting operation state.
[0088]
As described above, in the present embodiment, the compression operation and the cylinder resting operation is switched by a method different from that in Embodiment 1, but the present embodiment is same as Embodiment 1 in that the vane back chamber 25 is communicated with the lubricating oil storage 3a. Thus, in the present embodiment, too, the metal pieces 80 mixed in lubricating oil can be prevented from entering into the vane back chamber 25, thereby improving the reliability of the sliding part of the refrigerant compressor 100 and hence achieving reliable switching of the compression operation and the cylinder resting operation. [0089]
Embodiment 7
The following describes a vapor compression refrigeration cycle apparatus according to Embodiment 7 of the present invention. The refrigerant compressor
100 according to Embodiments 1 to 6 described above is used in a vapor compression refrigeration cycle apparatus described below, for example.
[0090]
Fig. 14 is a refrigerant circuit diagram illustrating the configuration of a vapor compression refrigeration cycle apparatus 500 according to the present embodiment. As illustrated in Fig. 14, the vapor compression refrigeration cycle apparatus 500 includes the refrigerant compressor 100 according to any one of Embodiments 1 to 6, a radiator 300 configured to radiate heat of refrigerant compressed by the refrigerant compressor 100, an expansion mechanism 200 configured to expand refrigerant flowing out of the radiator 300, and an evaporator 400 configured to allow refrigerant flowing out of the expansion mechanism 200 to receive heat.
[0091]
When the refrigerant compressor 100 according to any one of Embodiments 1 to 6 is included as in the vapor compression refrigeration cycle apparatus 500 according to the present embodiment, improvement can be achieved in reliability and energy saving performance in an actual load operation.
[0092]
As described above, the refrigerant compressor 100 according to Embodiments 1 to 6 described above includes the sealed container 3 storing lubricating oil, and the first compression mechanism 10 and the second compression mechanism 20 housed in the sealed container 3. The first compression mechanism 10 includes the first cylinder 11 including the first cylinder chamber 12, the first piston 13 configured to eccentrically rotate in the first cylinder chamber 12, the first vane 14 that includes the front end part 14a configured to contact the first piston 13 and is configured to divide the first cylinder chamber 12 into a plurality of spaces, the vane groove 19 formed in the first cylinder 11 and reciprocatingly housing the first vane 14, and the vane back chamber 15 formed on an outer peripheral side of the vane groove 19 in the first cylinder 11 and housing the rear end part 14b of the first vane 14. The second compression mechanism 20 includes the second cylinder 21 including the second cylinder chamber 22, the second piston 23 configured to eccentrically rotate in the second cylinder chamber 22, the second vane 24 that includes the front end part 24a configured to contact the second piston 23 and is configured to divide the second cylinder chamber 22 into a plurality of spaces, the vane groove 29 formed in the second cylinder 21 and reciprocatingly housing the second vane 24, and the vane back chamber 25 formed on an outer peripheral side of the vane groove 29 in the second cylinder 21 and housing the rear end part 24b of the second vane 24. The second compression mechanism 20 includes the cylinder resting mechanism 50 configured to switch the compression operation in which refrigerant is compressed with the front end part 24a of the second vane 24 being in contact with the second piston 23 and the cylinder resting operation in which refrigerant is not compressed with the front end part 24a of the second vane 24 being separated from the second piston 23. The cylinder resting mechanism 50 includes the magnetic body 53 that generates an attractive magnetic force attracting the second vane 24 in the direction separating from the second piston 23. The magnetic body 53 includes a first surface (for example, the surface 53a) facing the vane back chamber 25 and opposing to the rear end part 24b of the second vane 24. The second compression mechanism 20 includes an oilsupply passage (for example, the oilsupply passages 55a, 55b, 55c, 55d, and 55e) through which lubricating oil stored in the sealed container 3 is supplied to the vane back chamber 25 along a second surface (for example, the upper surface 53b, the lower surface 53c, the left side surface 53d, and the right side surface 53e) of the magnetic body 53, oriented differently from the first surface. The second surface (for example, the upper surface 53b, the lower surface 53c, the left side surface 53d, and the right side surface 53e) of the magnetic body 53 serves as a part of an internal wall surface of the oilsupply passage.
[0093]
With this configuration, the metal pieces 80 mixed in lubricating oil can be captured by the second surface of the magnetic body 53 before flowing into the vane back chamber 25, and thus can be prevented from entering into the vane back chamber 25. Consequently, the reliability of the sliding part can be improved. With this configuration, the metal pieces 80 can be captured before reaching the surface
53a of the magnetic body 53, and thus variation in the attractive magnetic force acting on the second vane 24 can be prevented. As a result, the compression operation and the cylinder resting operation can be reliably switched.
[0094]
In the refrigerant compressor 100 according to Embodiments 1 to 6 described above, the mesh members 56a, 56b, and 56c may be provided downstream of the second surface in the oilsupply passage.
[0095]
With this configuration, the metal pieces 80 that cannot be captured by the second surface of the magnetic body 53 can be captured by the mesh members 56a, 56b, and 56c, and thus can be more reliably prevented from entering into the vane back chamber 25.
[0096]
In the refrigerant compressor 100 according to Embodiments 1 to 6 described above, the mesh members 56a, 56b, and 56c may be made of a magnetic material and in contact with the magnetic body 53.
[0097]
With this configuration, the mesh members 56a, 56b, and 56c can be magnetized, and thus the effect of capturing the metal pieces 80 by the mesh members 56a, 56b, and 56c can be enhanced.
[0098]
In the refrigerant compressor 100 according to Embodiments 1 to 6 described above, the mesh members 56a and 56b may be provided upstream of the second surface in the oilsupply passage.
[0099]
With this configuration, the metal pieces 80 can be more reliably prevented from entering into the vane back chamber 25.
[0100]
In the refrigerant compressor 100 according to Embodiments 1 to 6 described above, the second compression mechanism 20 may further include the passage formation members 54a and 54b each opposing to the second surface of the magnetic body 53 and serving as another part of the internal wall surface of the oilsupply passage. In the refrigerant compressor 100 according to Embodiments 1 to 6 described above, the passage formation members 54a and 54b may be made of a non-magnetic material.
[0101]
With this configuration, the magnetic flux from the magnetic body 53 in the passage formation members 54a and 54b can be prevented from being dense, and thus the attractive magnetic force attracting the second vane 24 can be prevented from decreasing.
[0102]
In the refrigerant compressor 100 according to Embodiments 1 to 6 described above, the second cylinder 21 may serve as another part of the internal wall surface of the oilsupply passage.
[0103]
The vapor compression refrigeration cycle apparatus 500 according to Embodiment 7 described above includes the refrigerant compressor 100 according to Embodiments 1 to 6 described above, the radiator 300 configured to radiate heat of refrigerant compressed by the refrigerant compressor 100, the expansion mechanism 200 configured to expand refrigerant flowing out of the radiator 300, and the evaporator 400 configured to allow refrigerant flowing out of the expansion mechanism 200 to receive heat.
[0104]
With this configuration, improvement can be achieved in the reliability of the vapor compression refrigeration cycle apparatus 500 and energy saving performance in an actual load operation.
[0105]
Other embodiments
The present invention is not limited to the above-described embodiments and may be applicable to various kinds of modifications.
Although a vertical refrigerant compressor is described as an example in the above-described embodiments, the present invention is applicable to a horizontal refrigerant compressor.
[0106]
Although the configuration in which a mesh member is provided in an oilsupply passage is described as an example in the above-described embodiments, the mesh member may be omitted.
[0107]
The above-described embodiments and modifications may be combined with each other.
Reference Signs List [0108] compressor discharge pipe 3 sealed container 3a lubricating oil storage 4 intermediate dividing plate 5 drive shaft 5a long shaft part5b 5c, 5d eccentric pin shaft part 5e intermediate shaft part 6 6a inflow pipe 6b container short shaft part suction muffler internal space
6c, 6d outflow pipe 7 8 electric motor 8a rotor 8b stator 10 first compression
12a suction first vane mechanism 11 first cylinder 12 first cylinder chamber chamber 12b compression chamber 13 first piston
14a front end part 14b rear end part 15 vane back chamber 17 cylinder suction passage 18 discharge portl 9 vane groove 20 second compression mechanism 21 second cylinder 22 second cylinder chamber 23 second piston 24 second vane 24a front end part 24b rear end part25 vane back chamber 27 cylinder suction passage 28 discharge port29 vane groove 40 compression spring 50 cylinder resting mechanism 51 permanent magnet52 yoke 53 magnetic body 53a surface 53b upper surface 53c lower surface 53d left side surface 53e right side surface 54a, 54b passage formation member 55a, 55b, 55c, 55d, 55e oilsupply passage 55a1, 55b1, 55c1,55d1, 55e1 inflow port 56a, 56b, 56c mesh member 60 first support member60a bearing 60b flange part 63 discharge muffler 70 second support member 70a bearing 70b flange part 73 discharge muffler 80 metal piece 99 compression mechanism
100 refrigerant compressor 150 pressure switching valve 160 bypass pipe 200 expansion mechanism 300 radiator 400 evaporator 500 vapor compression refrigeration cycle apparatus

Claims (8)

  1. CLAIMS [Claim 1]
    A refrigerant compressor comprising: a sealed container storing lubricating oil; and a plurality of compression mechanisms housed in the sealed container, the plurality of compression mechanisms each including a cylinder including a cylinder chamber, a piston configured to eccentrically rotate in the cylinder chamber, a vane including a front end part configured to contact the piston and configured to divide the cylinder chamber into a plurality of spaces, a vane groove formed in the cylinder and reciprocatingly housing the vane, and a vane back chamber formed on an outer peripheral side of the vane groove in the cylinder and housing a rear end part of the vane, at least one of the plurality of compression mechanisms including a cylinder resting mechanism configured to switch a compression operation in which refrigerant is compressed with the front end part of the vane being in contact with the piston and a cylinder resting operation in which refrigerant is not compressed with the front end part of the vane being separated from the piston, the cylinder resting mechanism including a magnetic body generating an attractive magnetic force attracting the vane in a direction separating from the piston, the magnetic body including a first surface facing the vane back chamber and opposing to the rear end part of the vane, the at least one of the plurality of compression mechanisms including an oilsupply passage through which the lubricating oil stored in the sealed container is supplied to the vane back chamber along a second surface of the magnetic body, the second surface being oriented differently from the first surface, the second surface serving as a part of an internal wall surface of the oilsupply passage.
  2. [Claim 2]
    The refrigerant compressor of claim 1, wherein a mesh member is provided downstream of the second surface in the oilsupply passage.
  3. [Claim 3]
    The refrigerant compressor of claim 2, wherein the mesh member is made of a magnetic material and in contact with the magnetic body.
  4. [Claim 4]
    The refrigerant compressor of claim 1, wherein a mesh member is provided upstream of the second surface in the oilsupply passage.
  5. [Claim 5]
    The refrigerant compressor of any one of claims 1 to 4, wherein the at least one of the plurality of compression mechanisms further includes a passage formation member opposing to the second surface and serving as an other part of the internal wall surface of the oilsupply passage.
  6. [Claim 6]
    The refrigerant compressor of claim 5, wherein the passage formation member is made of a non-magnetic material.
  7. [Claim 7]
    The refrigerant compressor of any one of claims 1 to 6, wherein the cylinder serves as an other part of the internal wall surface of the oilsupply passage.
  8. [Claim 8]
    A vapor compression refrigeration cycle apparatus comprising the refrigerant compressor of any one of claims 1 to 7, a radiator configured to radiate heat of refrigerant compressed by the refrigerant compressor, an expansion mechanism configured to expand refrigerant flowing out of the radiator, and an evaporator configured to allow refrigerant flowing out of the expansion mechanism to receive heat.
GB1716656.2A 2015-05-14 2015-05-14 Refrigerant compressor and vapor compression refrigeration cycle apparatus including the same Expired - Fee Related GB2553711B (en)

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Citations (3)

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Publication number Priority date Publication date Assignee Title
US20080056923A1 (en) * 2006-08-30 2008-03-06 Samsung Electronics Co., Ltd. Rotary compressor
JP2010163926A (en) * 2009-01-14 2010-07-29 Toshiba Carrier Corp Multicylinder rotary compressor and refrigerating cycle apparatus
WO2012086779A1 (en) * 2010-12-24 2012-06-28 東芝キヤリア株式会社 Multi-cylinder rotary compressor and refrigeration cycle device

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Publication number Priority date Publication date Assignee Title
JP4504667B2 (en) * 2003-12-10 2010-07-14 東芝キヤリア株式会社 Refrigeration cycle equipment
JP5427583B2 (en) * 2009-12-16 2014-02-26 東芝キヤリア株式会社 Multi-cylinder rotary compressor and refrigeration cycle equipment
EP2990649B1 (en) * 2013-04-26 2018-11-14 Mitsubishi Electric Corporation Multi-cylinder rotary compressor and vapor compression refrigeration cycle device provided with multi-cylinder rotary compressor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080056923A1 (en) * 2006-08-30 2008-03-06 Samsung Electronics Co., Ltd. Rotary compressor
JP2010163926A (en) * 2009-01-14 2010-07-29 Toshiba Carrier Corp Multicylinder rotary compressor and refrigerating cycle apparatus
WO2012086779A1 (en) * 2010-12-24 2012-06-28 東芝キヤリア株式会社 Multi-cylinder rotary compressor and refrigeration cycle device

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WO2016181559A1 (en) 2016-11-17

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