RU2501978C1 - Double-staged rotary compressor - Google Patents

Double-staged rotary compressor Download PDF

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Publication number
RU2501978C1
RU2501978C1 RU2012122456/06A RU2012122456A RU2501978C1 RU 2501978 C1 RU2501978 C1 RU 2501978C1 RU 2012122456/06 A RU2012122456/06 A RU 2012122456/06A RU 2012122456 A RU2012122456 A RU 2012122456A RU 2501978 C1 RU2501978 C1 RU 2501978C1
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Russia
Prior art keywords
pressure stage
stage
low pressure
low
compression
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RU2012122456/06A
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Russian (ru)
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RU2012122456A (en
Inventor
Ацуеси ФУКАЯ
Масао ТАНИ
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Мицубиси Электрик Корпорейшн
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Priority to JP2011165094A priority patent/JP5586537B2/en
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Publication of RU2012122456A publication Critical patent/RU2012122456A/en
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Publication of RU2501978C1 publication Critical patent/RU2501978C1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00Combinations 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
    • F04C23/008Hermetic pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30Rotary-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
    • F04C18/34Rotary-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
    • F04C18/356Rotary-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
    • F04C18/3562Rotary-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
    • F04C18/3564Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00Combinations 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
    • F04C23/001Combinations 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/06Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • F04C28/065Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Abstract

FIELD: machine building.
SUBSTANCE: double-staged compressor 100, which is a double-staged rotary compressor with internal high pressure, includes a cover 19 of a low pressure stage, which closes an outlet hole 16 of the low pressure stage and forms inside an outlet space 20 of the low pressure stage. The compressor 100 is made with an intermediate channel 51 in a compression mechanism 3, and this channel connects the outlet space 20 of the low pressure stage and a compression chamber 35 of the high pressure stage. The compressor 100 is equipped with a relief mechanism in the cover 19 of the low pressure stage. The relief mechanism opens, when the load is less than the pre-determined load, and at the same time it connects the outlet space 20 of the low pressure stage and the space 53, in which the outlet pressure is maintained.
EFFECT: provision of suppression of pressure pulsations in an intermediate channel and for prevention of operation efficiency drop during operation under low load.
7 cl, 7 dwg

Description

FIELD OF THE INVENTION
This invention relates to a two-stage rotary compressor with two compression units.
State of the art
There is still a two-stage rotary compressor equipped with two compression units (a low-pressure stage compression unit and a high-pressure stage compression unit) in a compression mechanism in which a low-pressure stage compression unit and a high-pressure stage compression unit are connected in series. In this type of two-stage rotary compressor, the low-pressure stage compressor unit compresses the refrigerant that is sucked from the heat pump cycle to a specific pressure (maximum pressure). This maximum pressure is determined by the configuration of the space of the compression chamber of the compression unit of the low-pressure stage and the space of the compression chamber of the compression unit of the high-pressure stage. The compression unit of the high pressure stage additionally compresses the refrigerant, which is compressed in the compression unit of the low pressure stage. In addition, in a two-stage rotary compressor with internal high pressure, the refrigerant, which is compressed in the compression unit of the high pressure stage, is discharged into the interior of the sealed tank and discharged into the heat pump cycle from the interior of the sealed tank.
In a conventional two-stage internal high pressure rotary compressor, an intermediate channel is formed that extends around the outer surface of the sealed container to introduce intermediate pressure refrigerant compressed in the refrigeration unit of the low pressure stage into the refrigeration unit of the high pressure stage.
However, in a conventional two-stage rotary compressor, which is made with an intermediate channel passing around the outer surface of the sealed container, the intermediate channel is too long. As a result, when the refrigerant located in the intermediate channel is introduced into the refrigeration unit of the high pressure stage, the traceability becomes insufficient, and pressure pulsation is caused in the intermediate channel. Unfortunately, a sufficient effect of suppressing pressure pulsation is not obtained.
Therefore, a conventional two-stage rotary compressor with internal high pressure was proposed having an intermediate channel made in a sealed container.
As for conventional two-stage rotary compressors, a two-stage rotary compressor is proposed, made with an exhaust space enclosed in an intermediate channel separating the compression unit of the high pressure stage and the compression unit of the low pressure stage. Intermediate pressure refrigerant (the refrigerant that is discharged from the compression unit of the low pressure stage) is discharged into the discharge space to prevent excessive release of the intermediate pressure refrigerant to the compression unit of the high pressure stage (see, for example, Patent Document 1).
In addition, in connection with conventional two-stage rotary compressors, we note that a two-stage rotary compressor is proposed, equipped with an intermediate channel in the compression mechanism due to phase displacement of the inlet of the compression unit of the high pressure stage and the inlet of the compression unit of the low pressure stage (see, for example, patent document 2).
In addition, in connection with conventional two-stage rotary compressors, we note that a two-stage rotary compressor is proposed, equipped with an intermediate channel passing through the compression mechanism due to the location of the intermediate channel between the groove for the blade and the inlet channels of the low pressure stage and high pressure stage (see, for example Patent Document 3).
List of references
Patent Literature
Patent Document 1: Publication No. 2000-87892 of an Unexamined Japanese Patent Application
Patent Document 2: Publication No. 2007-113542 of the Unexamined Japanese Patent Application
Patent Document 3: Publication No. 2010-156226 of the Unexamined Japanese Patent Application
Summary of the invention
Technical challenge
In a heat pump installation (heat pump cycle) where a compressor is used, situations arise in which the pressure of the refrigerant discharged from the compressor (in other words, the pressure of the refrigerant flowing into the condenser) may turn out to be low, for example, when the load is low. However, in conventional two-stage rotary compressors made with an intermediate channel in the compression mechanism (see, for example, patent documents 1-3), low-load operation, such as described above, is not taken into account. Thus, the pressure of the refrigerant discharged from the two-stage rotary pump is higher than the required pressure, which leads to over-compression conditions. Accordingly, the operational efficiency of conventional two-stage rotary compressors made with an intermediate channel in the compression mechanism unfavorably falls during operation at low load.
In addition, since the two-stage rotary compressor described in Patent Document 1 is configured with an exhaust space in the intermediate plate, while the exhaust plate is discharged with intermediate pressure refrigerant, the distance between the bearings of the compression mechanism (the distance between the bearings rotatably supporting the drive shaft and provided at the upper and lower ends of the compression mechanism) becomes large. Accordingly, since in the two-stage rotary compressor described in Patent Document 1, the deviation of the compressor flow increases when the refrigerant load acts on the compression chamber, the reliability of the bearings is adversely reduced.
In addition, since the two-stage rotary compressor described in Patent Document 2 shifts the phases of the inlet of the compression unit of the high-pressure stage and the inlet of the compression unit of the low-pressure stage, the compression ratio adversely decreases due to an increase in dead space in the compression chamber of the compression unit of the high-pressure stage .
In addition, since the installation area of the intermediate channel of the two-stage rotary compressor described in Patent Document 3 is small, a limitation of the channel area in the intermediate channel occurs, which adversely leads to a drop in efficiency due to pressure loss.
This invention is made in order to solve at least one of the above problems, and its task is to develop a two-stage rotary compressor, which is configured to increase the tracking ability of the refrigerant introduced into the compression unit of the high pressure stage, as a result of which the pressure pulsation in the intermediate channel is suppressed, and also consists in developing a two-stage rotary compressor, which is made with the possibility of preventing the fall of pluatatsionnogo efficiency during low load operation.
The solution of the problem
A two-stage rotary compressor in accordance with the invention includes: a sealed container; a compression mechanism in a sealed container; an electric motor in a sealed container and a source of driving force of the compression mechanism; and a drive shaft transmitting the driving force of the electric motor to the compression mechanism, the compression mechanism having a low-pressure stage frame, a low-pressure stage cylinder, in which a first through hole is formed, which is a compression chamber of the low-pressure stage, and one opening of the first through hole is blocked by a frame low pressure stage, an intermediate partition that overlaps another opening of the first through hole, the cylinder of the high pressure stage, in which but the second through hole, which is the compression chamber of the high pressure stage, and one opening of the second through hole is blocked by an intermediate partition, the frame of the high pressure stage, which overlaps the other opening of the second through hole, the rolling piston of the low pressure stage, provided on the eccentric section of the drive shaft and making an eccentric rotational movement in the inner space of the compression chamber of the low-pressure stage, the rolling piston of the stage and high pressure provided on the eccentric portion of the drive shaft, wherein the rolling piston of the high pressure stage eccentricly rotates in the inner space of the compression chamber of the high pressure stage, the blade of the low pressure stage, dividing the inner space of the compression chamber of the low pressure stage into the suction space and the compression space, and the blade of the high-pressure stage dividing the inner space of the compression chamber of the high-pressure stage o pressure on the suction space and the compression space, as well as the compression unit of the low pressure stage and the compression unit of the high pressure stage, formed by vertical assembly in the following order - the frame of the low pressure stage, the cylinder of the low pressure stage, the intermediate partition, the cylinder of the high pressure stage and the frame high pressure stages. A two-stage rotary compressor compresses the refrigerant sucked from the pipe connected to the inlet of the low pressure stage of the compression chamber of the low pressure stage of the compression unit of the low pressure stage, in the compression chamber of the low pressure stage, re-compresses the refrigerant introduced into the compression chamber of the high pressure stage through the intermediate channel, and releases the refrigerant compressed in the compression chamber of the high-pressure stage into the space where the outlet pressure is maintained which is the interior of the sealed container.
In the two-stage rotary compressor, in the frame of the low-pressure stage, an outlet of the low-pressure stage is made, releasing refrigerant, which is compressed in the compression chamber of the low-pressure stage, a cover of the low-pressure stage is provided that covers the outlet of the low-pressure stage, and the cover of the low-pressure stage forms an outlet the space of the low pressure stage, the intermediate channel is made passing through the frame of the low pressure stage, the cylinder of the low pressure stage and an intermediate partition, wherein the intermediate channel connects the outlet space of the low pressure stage and the compression chamber of the high pressure stage, and the bypass mechanism provided in the cover of the low pressure stage opens, connecting the outlet space of the low pressure stage and the space where the outlet pressure is maintained when the load is less than a predetermined load.
In addition, in the two-stage rotary compressor, the bypass mechanism opens when the pressure in the outlet space of the low-pressure stage becomes equal to the pressure in the space where the outlet pressure is maintained, or exceeds it by a predetermined amount.
In addition, in the two-stage rotary compressor in the compression mechanism, the low pressure stage compression unit is located above the high pressure stage compression unit, and the bypass mechanism includes a bypass hole made in the cover of the low pressure stage, a valve configured to close the bypass hole, wherein said valve deforms and opens a bypass hole when a pressure equal to or greater than a predetermined value is applied to the valve.
In addition, in a two-stage rotary compressor, when the central axis of the drive shaft is taken as the reference point, and the direction of rotation from the outlet of the low-pressure stage to the bypass mechanism with a shorter distance is taken as the forward direction, the hole of the intermediate channel leading to the said outlet space of the low-pressure stage , made downstream than the bypass mechanism, in the forward direction.
In addition, a pipe is connected in the two-stage rotary compressor, which injects refrigerant into said outlet space of the low pressure stage.
In addition, in a two-stage rotary compressor, the refrigerant inlet position of the compression chamber of the low pressure stage and the refrigerant inlet position of the compression chamber of the high pressure stage are essentially in the same phase.
In addition, in a two-stage rotary compressor, when the central axis of the drive shaft is taken as the reference point, and the direction of rotation from the blade of the low pressure stage to the inlet with a shortened distance is taken as the forward direction, the intermediate channel is made downstream than the mentioned inlet, in forward direction.
Beneficial effects of the invention
The two-stage rotary compressor in accordance with this invention forms an intermediate channel in the compression mechanism, and this intermediate channel does not extend beyond the hermetic container, and therefore, said compressor is configured to reduce this intermediate channel. Accordingly, the traceability of the refrigerant introduced into the compression unit of the high pressure stage can be improved, and pressure pulsation in the intermediate passage can be suppressed.
In addition, the two-stage rotary compressor in accordance with this invention is equipped with a bypass mechanism that opens when the load is less than a predetermined load, and which connects the outlet space of the low pressure stage with the space where the outlet pressure is maintained. Accordingly, the refrigerant, which is compressed by the compression unit of the low pressure stage, can be bypassed (the compression unit of the high pressure stage) and released into the heat pump cycle without compression by the compression unit of the high pressure stage during operation at low load. Thus, the two-stage rotary compressor in accordance with this invention is configured to reduce the total compression losses generated during operation at low load, and to prevent the drop in operational efficiency during operation at low load.
Brief Description of the Drawings
1 is a longitudinal sectional view illustrating a two-stage compressor in accordance with an embodiment of the present invention.
FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1.
FIG. 3 is a cross-sectional view taken along line B-B of FIG. 1.
Fig. 4 is a cross-sectional view taken along line C-C of Fig. 1.
Figure 5 presents a cross section drawn along the line D-D according to figure 1.
FIG. 6 is a cross-sectional view taken along the line E-E of FIG. 1.
7 is a bar graph comparing the operational efficiencies of a two-stage compressor in accordance with an embodiment of the present invention and a conventional two-stage rotary compressor.
Description of Embodiments
Option exercise
Now, the configuration of a possible two-stage rotary compressor (two-stage compressor 100) in accordance with the invention will be sequentially described.
1 is a longitudinal sectional view illustrating a two-stage compressor in accordance with an embodiment of the present invention. In addition, FIG. 2 is a cross-sectional view taken along line AA of FIG. 1, FIG. 3 is a cross-sectional view taken along line BB of FIG. 1, FIG. 4 is a cross-sectional view taken along line CC according to FIG. figure 1, figure 5 shows a cross section drawn along the line DD according to figure 1, and figure 6 shows a cross section drawn along the line EE according to figure 1. Note that to facilitate understanding of the configuration of the two-stage compressor 100, FIG. 1 is a drawing in which the combined cross-sectional areas are separated in a plurality of positions. Accordingly, the exact positions of each component in a plan or bottom view will be the positions shown in FIGS. 2 to 6.
The two-stage compressor 100 in accordance with an embodiment includes two compression units (a compression unit 10 of a low pressure stage and a compression unit 30 of a high pressure stage) in a compression mechanism 3. This two-stage compressor 100 includes an electric motor 2 (motor assembly), a compression unit 10 stages of low pressure, compression unit 30 stages of high pressure, cover 19 stages of low pressure, cover 39 stages of high pressure, frame 14 stages low pressure frame 34 high-pressure stage, an intermediate partition wall 50, drive shaft 4, and the like In particular, in the sealed container 1, in the following order, the cover 39 of the high-pressure stage, the frame 34 of the high-pressure stage, the compression unit 30 of the high-pressure stage, the intermediate partition 50, the compression unit 10 of the low-pressure stage, the frame 14 of the low-pressure stage, are located 19 low-pressure stages and an electric motor 2. In addition, a drive shaft 4 is provided along the vertical direction of the sealed container 1, and in the lower part of the sealed container (that is, at the lower end portion and the drive shaft 4) is part 6 for storing the lubricating oil, the lubricating oil collects 6a. This lubricating oil 6a lubricates the compression mechanism 3, bearings, and the like.
The compression unit 10 of the low pressure stage of the compression mechanism 3 includes a cylinder 11 of the low pressure stage, a rolling piston 12 of the low pressure stage, a blade 26 of the low pressure stage (see FIG. 4), and the like. The cylinder 11 of the low-pressure stage is a substantially plate-shaped element and has a through hole of substantially cylindrical geometry, made essentially in the central part, which serves as the compression chamber 15 of the low-pressure stage. The upper opening of this through hole is blocked by the low pressure stage frame 14, and its lower opening is blocked by the intermediate partition 50, limiting the compression chamber 15 of the low pressure stage. In addition, in the compression chamber 15 of the low-pressure stage, the inlet 21 of the low-pressure stage and the outlet 16 of the low-pressure stage made in the frame 14 of the low-pressure stage are in communication. The inlet 21 of the low pressure stage is connected to the inlet pipe 8 by means of a connecting pipe 9 and an intake silencer 7, which are provided outside the sealed container 1. That is, the inlet 21 of the low pressure stage is connected to the low pressure side of the heat pump cycle. In addition, the outlet 16 of the low-pressure stage is equipped with a plate valve, which is a plate-shaped outlet valve 17 of the low pressure stage, and a valve stop 18 of the low-pressure stage valve mounted with rivet 18a (see FIG. 3). By raising the exhaust valve 17 of the low pressure stage, which is a plate valve, and opening the outlet 16 of the low pressure stage, the compression chamber 15 of the low pressure stage is connected to the outlet space 20 of the low pressure stage, which will be described later.
The compression chamber 15 of the low pressure stage is equipped with a rolling piston 12 of the low pressure stage and a blade 26 of the low pressure stage. The rolling piston 12 of the low pressure stage has a substantially cylindrical geometry and is mounted on the eccentric portion of the drive shaft 4. The blade 26 of the low pressure stage is slidable in the groove 27 for the blade of the low pressure stage made in the cylinder 11 of the low pressure stage. In addition, the blade 26 of the low pressure stage is deflected to the drive shaft 4 by a deflecting element, such as a spring, while the edge of the blade 26 of the low pressure stage is configured to follow the periphery of the rolling piston 12 of the low pressure stage. Essentially, the compression chamber 15 of the low pressure stage is divided into a suction space in communication with the inlet 21 of the low pressure stage and a compression space in communication with the outlet 16 of the low pressure stage. As can be understood from FIG. 3 and FIG. 4, the inlet 21 of the low pressure stage of the compression chamber 15 of the low pressure stage communicates with the compression chamber 15 of the low pressure stage in the vicinity of the left side of the blade 26 of the low pressure stage, when viewed in plan view. In addition, the outlet 16 of the low pressure stage communicates with the compression chamber 15 of the low pressure stage in the vicinity of the right side of the blade 26 of the low pressure stage, when viewed in plan view.
The compression unit 30 of the high-pressure stage includes a cylinder 31 of the high-pressure stage, a rolling piston 32 of the high-pressure stage, a blade 42 of the high-pressure stage (see FIG. 5), and the like. The cylinder 31 of the high-pressure stage has a substantially plate-like shape and has a through hole of substantially cylindrical geometry, made essentially in the central part, which serves as a compression chamber 35 of the high-pressure stage. The upper opening of this through hole is blocked by an intermediate partition 50, and its lower opening is blocked by the frame 34 of the high-pressure stage, limiting the compression chamber 35 of the high-pressure stage. The compression chamber 35 of the high pressure stage is made having a smaller volume than the compression chamber 15 of the low pressure stage. In addition, in the compression chamber 35 of the high-pressure stage, the inlet 41 of the high-pressure stage made in the cylinder 31 of the high-pressure stage and the outlet 36 of the high-pressure stage made in the frame 34 of the high-pressure stage are in communication with each other. The inlet 41 of the high-pressure stage of the compression unit 30 of the high-pressure stage is adapted to communicate with the outlet 16 of the low-pressure stage of the compression unit 10 of the low-pressure stage by means of the subsequently described outlet space 20 of the low-pressure stage and the intermediate channel 51. In addition, the outlet 36 of the stage high pressure is equipped with a plate valve, which is a plate-shaped exhaust valve 37 high-pressure stage and a valve 38 stroke limiter of the low pressure stage installed with rivet 38a (see FIG. 6). By raising the exhaust valve 37 of the high-pressure stage of the plate valve and opening the outlet 36 of the high-pressure stage, the compression chamber 35 of the high-pressure stage communicates with the outlet space 40 of the high-pressure stage, which will be described later.
The compression chamber 35 of the high-pressure stage is equipped with a rolling piston 32 of the high-pressure stage and a blade 42 of the high-pressure stage. The rolling piston 32 of the high-pressure stage has a substantially cylindrical geometry and is mounted on the eccentric portion of the drive shaft 4. In this embodiment, the rolling piston 32 of the high-pressure stage has a substantially opposite phase (position rotated substantially 180 degrees around the axis of rotation of the drive shaft 4) with respect to the rolling piston 12 of the low pressure stage, when viewed in plan view. The blade 42 of the high-pressure stage is slidable in the groove 43 for the blade of the high-pressure stage, made in the cylinder 31 of the high-pressure stage. In addition, the blade 42 of the high-pressure stage is deflected to the drive shaft 4 by a deflecting element, such as a spring, while the edge of the blade 42 of the high-pressure stage is configured to follow the periphery of the rolling piston 32 of the high-pressure stage. Essentially, the compression chamber 35 of the high pressure stage is divided into a suction space in communication with the inlet 41 of the high pressure stage and a compression space in communication with the outlet 36 of the high pressure stage. As can be understood from FIGS. 5 and 6, the inlet 41 of the high-pressure stage of the compression chamber 35 of the high-pressure stage is in communication with the compression chamber 35 of the high-pressure stage in the vicinity of the left side of the blade 42 of the high-pressure stage, when viewed in plan view. In addition, the outlet 36 of the high-pressure stage communicates with the compression chamber 35 of the high-pressure stage in the vicinity of the right side of the blade 42 of the high-pressure stage, when viewed in plan view.
In addition, as can be understood from FIGS. 3-6, the inlet 21 of the low pressure stage of the compression chamber 15 of the low pressure stage and the inlet 41 of the high pressure stage of the compression chamber 35 of the high pressure stage are essentially in the same phase, if you look at the plan view. The outlet 16 of the low pressure stage and the outlet 36 of the high pressure stage are essentially in the same phase when viewed in plan view. Accordingly, the two-stage compressor 100 in accordance with an embodiment differs from the two-stage rotary compressor described in Patent Document 2 in that the dead space in the compression chamber 35 of the high-pressure stage does not increase and the compression ratio does not fall.
The frame 14 of the low-pressure stage includes an upper bearing and serves to rotate essentially the middle portion of the drive shaft 4. In the frame 14 of the low-pressure stage, as mentioned above, the outlet 16 of the low-pressure stage of the compression unit 10 of the low stage is made pressure. The cover 19 of the low-pressure stage is a bowl-shaped container, the opening of which is located in the lower part. This cover 19 of the low pressure stage is configured to close the outlet 16 of the low pressure stage from above and forms the outlet space 20 of the low pressure stage inside.
In addition, the intermediate channel 51 also communicates with the outlet space 20 of the low pressure stage. This intermediate channel 51 extends through the frame 14 of the low pressure stage, the cylinder 11 of the low pressure stage and the intermediate wall 50 in the vertical direction and connects the outlet space 20 of the low pressure stage and the inlet 41 of the high pressure stage. That is, the refrigerant that has flowed into the outlet space 20 of the low pressure stage is sucked into the compression unit 30 of the high pressure stage through an intermediate partition 50.
Note that, passing through the cylinder 11 of the low pressure stage, this intermediate channel 51 passes through a position that is on the left side of the blade 26 of the low pressure stage and which is a position spaced from the blade 26 of the low pressure stage (i.e., from the groove for vanes of the low pressure stage) further than the inlet 21 of the low pressure stage. In other words, taking the central axis of the drive shaft 4 as the reference point and assuming that the direction of rotation from the blade 26 of the low pressure stage to the inlet 21 of the low pressure stage on the short distance side is taken as the forward direction (the direction indicated by the arrow in figure 4), we find that the intermediate channel 51 is formed downstream than the inlet 21 of the low pressure stage, in the forward direction.
The frame 34 of the high-pressure stage includes a lower bearing and rotatably supports the lower end portion of the drive shaft 4. In the frame 34 of the high-pressure stage, as mentioned above, an outlet 36 of the high-pressure stage of the compression unit 30 of the high-pressure stage is formed. The lid 39 of the high-pressure stage is a bowl-shaped container, the opening of which is in the upper part. This cover 39 of the high-pressure stage is configured to close the outlet 36 of the high-pressure stage from below and forms the outlet 40 of the high-pressure stage inside.
In addition, in the outlet space 40 of the high-pressure stage, an outlet channel 52 is made, which communicates with the interior of the sealed container 1. This outlet channel 52 passes through the frame 34 of the high-pressure stage, cylinder 31 of the high-pressure stage, intermediate wall 50, cylinder 11 of the low-pressure stage and the frame 14 of the low pressure stage in the vertical direction and connects the outlet space 40 of the high pressure stage with the interior of the sealed container 1. That is, a two-stage compressor 1 00, in accordance with an embodiment, is an internal high pressure compressor in which the internal space of the sealed container 1 becomes the space 53 where the outlet pressure is maintained (during steady state operation, this is a space having a high pressure refrigerant pressure that is discharged from the compression unit 30 high pressure stage). For example, an exhaust pipe 5 is provided in the upper part of the sealed container 1, and a high pressure refrigerant that is discharged into the sealed container 1 is discharged out of this exhaust pipe 5. Note that, in plan view, this exhaust channel 52 passes through a point symmetrical the intermediate channel 51, when the Central axis of the drive shaft 4 is set as the reference point.
The electric motor 2 is a source of driving force for the compression unit 10 of the low pressure stage and the compression unit 30 of the high pressure stage. This electric motor 2 includes a stator 2a and a rotor 2b. The stator 2a has an essentially cylindrical geometry and is attached to the inner circumferential surface of the sealed container 1. The rotor 2b has an essentially cylindrical geometry and is located at the inner circumferential surface of the stator 2a, maintaining a predetermined gap with it. In addition, the upper end of the drive shaft 4 is fixed to the inner circumferential surface of the rotor 2b.
In addition, the two-stage compressor 100 in accordance with an embodiment is provided with an injector 60 in the cover 19 of the low pressure stage. One end of this injector 60 is open to the outlet space 20 of the low pressure stage, and the other end is connected to the discharge pipe 61. Note that the injector 60 is designed to pump refrigerant in the heat pump cycle not through the two-stage compressor 100 into the refrigerant that is discharged from the compression unit 10 low pressure stages. Accordingly, the joint position of the injector 60 is not limited to the cover 19 of the low pressure stage, but may be any position of the joint in the channel (exhaust space of the low pressure stage) to the point where the refrigerant which is discharged from the compression unit 10 of the low pressure stage is sucked into the compression unit 30 steps of a high pressure.
In addition, the two-stage compressor 100 in accordance with an embodiment has a bypass hole 23 provided in the cover 19 of the low pressure stage, while the bypass hole 23 connects the outlet space 20 of the low pressure stage and the space 53 where the outlet pressure is maintained, which is an airtight interior tanks 1. In addition, the bypass hole 23 is equipped with a plate valve, which is a plate-shaped bypass valve 24 and a stroke limiter 25 erepusknogo valve mounted via rivets 29 (see FIG. 2). The combination of these elements will be called a bypass mechanism.
Note that in the present embodiment, the positional relationship of the bypass hole 23 and the intermediate channel 51 is as shown in FIG. In other words, taking the central axis of the drive shaft 4 as the reference point and assuming that the direction of rotation from the blade 26 of the low pressure stage to the inlet 21 of the low pressure stage on the short distance side is taken as the forward direction (the direction indicated by the arrow in figure 2), we find that the intermediate channel 51 is formed downstream than the bypass hole 23, in the forward direction.
Next, operation of the two-stage compressor 100 will be described.
When applying power, the electric motor 2 is running. The electric motor 2 and the compression mechanism 3 are connected by the drive shaft 4, and the driving force that is generated by the electric motor 2 is transmitted to the compression mechanism 3 through the drive shaft 4. In particular, when powered, the rotor 2b of the electric motor 2 rotates. When the rotor 2b rotates, the drive shaft 4, which is fitted into the rotor 2b, also rotates. In addition, when the drive shaft 4 rotates, each of the rolling piston 12 of the low pressure stage and the rolling piston 32 of the high pressure stage, which are fitted in the drive shaft 4, rotates with eccentricity in the compression chamber 15 of the low pressure stage and the compression chamber 35 of the high pressure stage , respectively. When the rolling piston 12 of the low pressure stage and the rolling piston 32 of the high pressure stage rotate with an eccentricity, the refrigerant in the compression unit 10 of the low pressure stage and the compression unit 30 of the high pressure stage is compressed.
In a two-stage compressor 100, which operates as described above, the refrigerant flows as follows.
First, the low pressure refrigerant flows into the internal silencer 7 from the outside through the suction pipe 8. The low pressure refrigerant that flows into the internal silencer 7 is sucked into the compression chamber 15 of the low pressure stage through the connecting pipe 9. The low pressure refrigerant which flows into the compression chamber 15 of the stage low pressure, is compressed to an intermediate pressure in the compression chamber 15 of the low pressure stage. When the refrigerant is compressed to intermediate pressure, the low-pressure stage exhaust valve 17 opens due to the pressure difference between the refrigerant in the low-pressure stage compression chamber 15 and the refrigerant in the low-pressure stage exhaust chamber 20, and the refrigerant in the low-pressure stage compression chamber 15 is discharged the outlet 16 of the low pressure stage to the outlet 20 of the low pressure stage. In this case, the intermediate pressure is the pressure that is determined by the ratio between the volume of the suction space of the compression chamber 15 of the low pressure stage and the volume of the suction space of the compression chamber 35 of the high pressure stage.
The intermediate pressure refrigerant that is discharged into the exhaust space 20 of the low pressure stage is sucked into the compression chamber 35 of the high pressure stage through the intermediate channel 51. The intermediate pressure refrigerant, which has been sucked into the compression chamber 35 of the high pressure stage, is compressed to the outlet pressure in the compression chamber 35 high pressure stages. When the refrigerant is compressed to the outlet pressure, the high-pressure stage exhaust valve 37 opens due to the pressure difference between the refrigerant in the compression chamber 35 of the high-pressure stage and the refrigerant in the exhaust space 40 of the high-pressure stage, and the refrigerant located in the compression chamber 35 of the high-pressure stage is discharged the outlet 36 of the high pressure stage into the outlet 40 of the high pressure stage. The refrigerant under the outlet pressure, which is discharged into the outlet space 40 of the high pressure stage, is discharged into the space 53, where the outlet pressure is maintained, in the upward direction of the compression unit 10 of the low pressure stage through the outlet channel 52. Then, the refrigerant under the outlet pressure, which is discharged into the space 53 where the outlet pressure is maintained, is discharged out of the outlet pipe 5.
Note that when in a heat pump installation that is equipped with a two-stage compressor 100 (i.e., in a heat pump cycle where a two-stage compressor 100 is used), a discharge operation is performed, the injected refrigerant is pumped into the exhaust space 20 of the low pressure stage from the discharge pipe 61 through injector 60, which are shown in FIG. The injected refrigerant is mixed with intermediate pressure refrigerant discharged from the compression chamber 15 of the low pressure stage in the discharge space 20 of the low pressure stage and is compressed in the compression unit 30 of the high pressure stage.
When the load of the heat pump system is small (this situation in the following text is formulated as follows: “during operation at low load”), there are cases in which the state of excessive compression occurs, which is a state in which compression only in the compression unit 10 of the low pressure stage results in discharge pressure (in other words, the pressure at which the refrigerant flows into the condenser). That is, there are cases in which the aforementioned intermediate refrigerant pressure becomes higher than the desired outlet pressure. In these cases, the configuration of the two-stage compressor 100 in accordance with an embodiment is such that the bypass valve 24 opens due to the pressure difference between the refrigerant of the outlet space 20 of the low pressure stage and the refrigerant of the space 53 where the outlet pressure is maintained, and the refrigerant in the outlet the space 20 of the low pressure stage, is discharged into the space 53, where the outlet pressure is maintained, through the bypass hole 23. In other words, the configuration of the two-stage of the compressor 100 in accordance with an embodiment is such that the bypass valve 24 deforms and opens the bypass hole 23 when the pressure of the outlet space 20 of the low pressure stage becomes equal to or greater than the pressure of the space 53 where the outlet pressure is maintained. That is, the refrigerant that is discharged from the compression unit 10 of the low pressure stage to the outlet space 20 of the low pressure stage is bypassed and discharged into the space 53 where the outlet pressure is maintained without compression in the compression unit 30 of the high pressure stage.
When the state of excessive compression occurs, the outlet pressure is achieved by compressing only in the compression unit 10 of the low pressure stage, and compression by the compression unit 30 of the high pressure stage becomes unnecessary, and when the compression is carried out by the compression unit 30 of the high pressure stage, the efficiency drops. However, when the state of excessive compression occurs in the two-stage compressor 100, the refrigerant which is compressed in the compression unit 10 of the low pressure stage bypasses the compression unit 30 of the high pressure stage and is discharged. Thus, it is possible to suppress the loss (loss due to excessive compression) caused when the state of excessive compression occurs, and it is possible to increase the operational efficiency during operation at low load.
In addition, the two-stage compressor 100 in accordance with an embodiment is provided with a bypass hole 23 in the cover 19 of the low pressure stage. Accordingly, the refrigerant is discharged from the bypass port 23 into the space 53 where the outlet pressure is maintained, in the sealed container 1, without passing through the intermediate channel 51. That is, the refrigerant which is discharged from the bypass port 23 into the space 53 where the outlet pressure is maintained is discharged into this space 53, where the outlet pressure is maintained, from the bypass hole 23 without loss in compression, due to the passage through the intermediate channel 51. Thus, it is possible to suppress excess losses nom compression during operation at light load.
Note that, as mentioned above, on the underside of the sealed container 1, a lubricating oil storage part 6 is provided in which the lubricating oil 6a is enclosed. Since the lubricating oil 6a is supplied to the mechanical parts of the compression mechanism 3, in the aforementioned part there is enclosed an amount of oil into which the compression unit located on the upper side can be immersed (the compression unit 10 of the low pressure stage in FIG. 1). In the case of a typical two-stage rotary compressor (see Patent Documents 1-3), when the two-stage rotary compressor is arranged longitudinally, the low pressure stage compression unit is provided under the high pressure stage compression unit. Accordingly, as in the two-stage rotary compressors described in patent documents 2 and 3, that is, in the two-stage rotary compressor that releases refrigerant compressed in the compression unit of the low pressure stage into the cover of the low pressure stage (exhaust space of the low pressure stage), the outlet space of the low pressure stage is provided below the compression unit of the low pressure stage. That is, a low pressure stage cover is provided on the lower side of the compression unit of the low pressure stage. Thus, the cover of the low pressure stage is immersed in lubricating oil. In this case, when it is attempted to form a bypass port 23 according to an embodiment in the cover of the low pressure stage, the lubricating oil invades the outlet space of the low pressure stage from the bypass port 23. In addition, the lubricating oil is sucked when the refrigerant is discharged from the bypass port 23, and the outflow of lubricating oil from a two-stage rotary compressor unfavorably increases. Because of this, in a typical two-stage rotary compressor, it is not possible to form a bypass channel 23 according to an embodiment in the cover of the low pressure stage. Therefore, in the case of the two-stage rotary compressors described in patent documents 2 and 3, when the two-stage rotary compressor is placed longitudinally, there is no choice but to provide a bypass hole 23 in a narrow and thin channel that connects the exhaust space of the low pressure stage and the compression unit of the high stage pressure.
However, in the case of a two-stage compressor 100 in accordance with an embodiment where the two-stage compressor 100 is placed longitudinally, unlike typical compressors, a low pressure stage compression unit 10 is provided on the upper side of the high pressure stage compression unit 30. Accordingly, the outlet space 20 of the low pressure stage is provided on the upper side of the compression unit 10 of the low pressure stage, and the cover 19 of the low pressure stage can be positioned at a height where the cover 19 of the low pressure stage is not immersed in the lubricating oil 6a. As a result, the bypass hole 23 can be provided in the cover 19 of the low pressure stage.
Furthermore, since in the two-stage compressor 100 according to an embodiment, the bypass hole 23 is provided not in the intermediate channel 51 but in the cover 19 of the low pressure stage, the bypass valve 24 may be a plate valve with a simple design. Accordingly, it will be possible to use the same parts for the bypass valve 24 and the bypass valve limiter 25 that are used in the low pressure stage exhaust valve 17 and the low pressure stage valve limiter 18, the high pressure exhaust valve 37 and the high limit valve 38 pressure. By sharing the same parts, you can reduce the cost to a low level. In addition, since the design of the bypass valve 24 is simple, it will be possible to reduce assembly costs to a low level.
Next, features of the intermediate channel 51 of the two-stage compressor 100 in accordance with an embodiment will be described.
As mentioned above, the intermediate channel 51 passes through the frame 14 of the low pressure stage, the cylinder 11 of the low pressure stage and the intermediate wall 50 in the vertical direction and connects the outlet space 20 of the low pressure stage and the inlet 41 of the high pressure stage. That is, the refrigerant that is compressed in the compression unit 10 of the low pressure stage flows into the intermediate channel 51 after the low pressure stage 20 is discharged into the exhaust space 20. Accordingly, unlike the two-stage rotary compressor described in Patent Document 1, it is not necessary to form an outlet space for the compression unit 10 of the low-pressure stage in the intermediate wall 50. Thus, in contrast to the two-stage rotary compressor described in Patent Document 1, the two-stage the compressor 100 in accordance with the embodiment, it is possible to reduce the distance between the frame 14 of the low pressure stage, which also acts as a bearing for one shaft 4, and the frame 34 of the high pressure stage, and to increase the reliability of the two-stage compressor 100 (in particular, the reliability of the frame 14 of the low pressure stage and the frame 34 of the high pressure stage).
In addition, the intermediate channel 51 is made in a position that is further from the blade 26 of the low pressure stage (in other words, the groove 27 for the blade of the low pressure stage) than the inlet 21 of the low pressure stage, that is, in a position that is not between an inlet 21 of the low pressure stage and a blade 26 of the low pressure stage (in other words, a groove 27 for the blade of the low pressure stage). Accordingly, unlike the intermediate channel described in Patent Document 3, the intermediate channel 51 according to an embodiment can guarantee a large channel area and eliminate the main cause of pressure losses resulting in a drop in efficiency. In addition, since the intermediate channel 51 does not interfere with the functions of the inlet 21 of the low pressure stage and the blade 26 of the low pressure stage (in other words, the groove 27 for the blade of the low pressure stage), the installation versatility of the channel increases. Note that, although FIG. 4 and other drawings show an intermediate channel 51 having an opening of substantially cylindrical geometry, any opening with an area larger than that of the outlet 16 of the low pressure stage can be used.
Depending on the refrigerant and the magnitude or smallness of the density of the refrigerant flowing into the intermediate channel, pressure pulsation occurs. In particular, in a two-stage rotary compressor controlled by an inverter, there is a tendency for pressure pulsation to occur due to an increase and decrease in rotation speed. In a conventional two-stage rotary compressor, which provides for the placement of the intermediate channel outside the sealed container, since the traceability of the refrigerant introduced into the compression unit of the high pressure stage is unsatisfactory, in order to get rid of the pressure pulsation in the intermediate channel due to resonance, a configuration involving flow pipes with different pipe lengths. However, since the two-stage compressor 100 in accordance with an embodiment provides an intermediate channel 51 in the compression mechanism 3 and reduces the channel length, the traceability of the refrigerant introduced into the compression unit 30 of the high pressure stage from the compression unit 10 of the low pressure stage increases and the pressure pulsation suppressed, resulting in increased operational efficiency.
As mentioned above, taking the central axis of the drive shaft 4 as the reference point and assuming that the direction of rotation from the outlet 16 of the low pressure stage to the bypass hole 23 on the short distance side is taken as the forward direction (the direction indicated by the arrow in figure 2), we obtain that the intermediate channel 51 is formed lower than the bypass hole 23, in the forward direction. This forward direction is the direction of the main refrigerant stream flowing from the outlet 16 of the low pressure stage to the bypass port 23. By placing the bypass port 23 and the intermediate channel 51 with this positional relationship, the refrigerant is in an over-compressed state that is discharged from the compression unit 10 of the stage low pressure, is discharged into the sealed container through the bypass hole 23 before it reaches the intermediate channel 51 through the bypass mechanism (bypass th holes 23, 24 and the bypass Kapan stroke limiter 25 bypass Kapan). Accordingly, the refrigerant that is discharged through the space 53 supported under the outlet pressure is reliably discharged into this space supported under the outlet pressure without passing through the intermediate channel 51, and the beneficial effect of the bypass mechanism is increased. On the other hand, even if a conventional two-stage rotary compressor, which provides for the placement of the intermediate channel outside the sealed container 1, is equipped with a bypass mechanism (bypass mechanism provided in the cover of the low pressure stage), since the channel length characteristic of the intermediate channel is large, the refrigerant is in a state excessive compression cannot be completely discharged from the bypass hole 23, and part of the refrigerant in the state of excessive compression flows into the compression unit of the high stage who pressure, causing unnecessary compression, resulting in a drop in efficiency.
In conclusion, the effect of increasing the operational efficiency of the two-stage compressor 100 in accordance with an embodiment will be described.
Fig. 7 is a bar graph comparing the operational efficiencies of a two-stage compressor in accordance with an embodiment and a conventional two-stage rotary compressor. Note that the conventional two-stage rotary compressor shown in Fig. 7 is a two-stage rotary compressor with internal high pressure, which provides for the placement of the intermediate channel outside the sealed container and is not equipped with a bypass mechanism, like the compressor in the embodiment. Furthermore, in the drawing, the operational efficiency of a two-stage compressor 100 according to an embodiment is shown taking into account that the operational efficiency of a conventional two-stage rotary compressor is taken as a reference value (100%).
When comparing the operational efficiency during steady state operation (nominal conditions shown in FIG. 7), the operational efficiency of the two-stage compressor 100 according to the embodiment is 102%, and the operational efficiency is increased by about 2% compared with a conventional two-stage rotary compressor . From this result it is clear that by forming the intermediate channel 51 in the compression mechanism 3, the traceability of the refrigerant introduced into the compression unit 30 of the high pressure stage is increased, and pressure pulsation in the intermediate channel can be suppressed, which leads to an increase in operational efficiency.
When comparing the operational efficiency during operation at low load (low load conditions shown in FIG. 7), the operational efficiency of the two-stage compressor 100 according to the embodiment is 101.5%, and the operational efficiency is increased by about 1.5% compared to with a conventional two-stage rotary compressor. From this result it is clear that in the two-stage compressor 100 in accordance with an embodiment, due to the presence of a bypass mechanism (bypass hole 23, bypass valve 24 and bypass stroke limiter 25) in the low pressure stage cover 19, it becomes possible to direct refrigerant, which is compressed in the compression unit 10 of the low pressure stage, bypassing the compression unit 30 of the high pressure stage and discharging, which leads to increased operational efficiency.
Note that, since in the two-stage compressor 100, which is made with an intermediate channel 51 in the compression mechanism 3, the component, which is an intermediate channel, does not extend beyond the sealed container 1, it is possible to obtain a useful effect, such as miniaturization, ease of packaging and transportation, ease of disassembly, etc.
List of drawings
1. sealed container;
2. electric motor;
2a. stator; 2b. rotor;
3. compression mechanism;
4. drive shaft;
5. exhaust pipe;
6. part for the storage of lubricating oil;
6a. lubricating oil;
7. intake silencer;
8. suction pipe;
9. connecting pipe;
10. compression block stage low pressure;
11. low stage cylinder;
12. a rolling piston of a low pressure stage;
14. low pressure stage frame;
15. compression chamber of the low pressure stage;
16. the outlet of the low pressure stage;
17. low pressure stage valve;
18. valve stop valve low pressure stage;
18a. rivet;
19. cover for low pressure stage;
20. the outlet space of the low pressure stage;
21. the inlet of the low pressure stage;
23. bypass hole;
24. bypass valve;
25. overflow valve stroke limiter;
26. the blade of the low pressure stage;
27. groove for the blade stage low pressure;
29. rivet;
30. compression block stage high pressure;
31. cylinder high pressure stage;
32. rolling piston of a high pressure stage;
34. high pressure stage frame;
35. compression chamber of the high pressure stage;
36. the outlet of the high pressure stage;
37. high pressure stage valve;
38. valve stroke limiter high pressure stage; 38a. rivet;
39. high pressure stage cover;
40. the outlet space of the high pressure stage;
41. inlet of the high pressure stage;
42. the blade of the high pressure stage;
43. groove for the blades of the high pressure stage;
50. intermediate partition;
52. exhaust channel;
53. the space in which the outlet pressure is maintained;
60. injector;
61. discharge pipe;
100. two-stage compressor.

Claims (7)

1. A two-stage rotary compressor (100), comprising: a sealed container (1); a compression mechanism (3) located in a sealed container (1); an electric motor (2) located in a sealed container (1) and which is the source of the driving force of the compression mechanism (3); and a drive shaft (5) transmitting the driving force of the electric motor (2) to the compression mechanism (3), wherein the compression mechanism (3) includes a frame (14) of the low pressure stage, a cylinder (11) of the low pressure stage, in which the first through a hole representing the compression chamber (15) of the low pressure stage, and one opening of the first through hole is blocked by a frame (14) of the low pressure stage, an intermediate partition (50) that overlaps another opening of the first through hole, the cylinder (31) of the stage high pressure, in which a second through hole is made, which is a compression chamber (35) of the high pressure stage, and one opening of the second through hole is closed by an intermediate partition (50), a frame (34) of the high pressure stage, which overlaps another opening of the second through holes, rolling piston (12) of the low pressure stage, provided on the eccentric portion of the drive shaft (5) and performing an eccentric rotational movement in the inner space of the compression chamber (15) low pressure blunts, a rolling piston (32) of the high pressure stage provided on the eccentric section of the drive shaft (5) and performing an eccentric rotational movement in the inner space of the compression chamber (35) of the high pressure stage, a blade (26) of the low pressure stage separating the inner the space of the compression chamber (15) of the low-pressure stage to the suction space and the compression space, and the blade (42) of the high-pressure stage separating the said inner spaces about the compression chamber (35) of the high pressure stage to the suction space and the compression space, and the compression unit (10) of the low pressure stage and the compression unit (30) of the high pressure stage formed by vertical assembly in the following order - frame (14) of the low pressure stage , cylinder (11) of the low pressure stage, intermediate partition (50), cylinder (31) of the high pressure stage and frame (34) of the high pressure stage, the two-stage rotary compressor compresses the refrigerant sucked from the pipe, single to the low pressure stage inlet (21) of the compression chamber (15) of the low pressure stage of the compression unit (10) of the low pressure stage, in the compression chamber (15) of the low pressure stage, re-compresses the refrigerant introduced into the compression chamber (35) of the high stage pressure through the intermediate channel, and releases the refrigerant compressed in the compression chamber (35) of the high-pressure stage into the space (53), where the outlet pressure is maintained, and which is the inner space of the sealed container ty (1), while in the frame (14) of the low pressure stage, an outlet (16) of the low pressure stage is made, releasing refrigerant, which is compressed in the compression chamber (15) of the low pressure stage, a cover (19) of the low pressure stage is provided to cover the outlet (16) of the low-pressure stage, the cover (19) of the low-pressure stage forming inside the outlet space of the low-pressure stage, said intermediate channel being passed through the frame (14) of the low-pressure stage, the cylinder (11) of the low-pressure stage and an intermediate partition (50), wherein said intermediate channel connects the outlet space of the low-pressure stage and the compression chamber (35) of the high-pressure stage, and the bypass mechanism provided in the cover (19) of the low-pressure stage opens, connecting the said outlet space of the stage low pressure and the space (53) where the outlet pressure is maintained when the load is less than a predetermined load.
2. The two-stage rotary compressor (100) according to claim 1, in which the bypass mechanism opens when the pressure in the outlet space of the low-pressure stage becomes equal to the pressure in the space (53) where the outlet pressure is maintained, or exceeds it by a predetermined value.
3. A two-stage rotary compressor (100) according to claim 2, wherein in the compression mechanism (3) the compression unit (10) of the low pressure stage is located above the compression unit (30) of the high pressure stage, and the bypass mechanism includes a bypass hole (23 ), made in the cover (19) of the low pressure stage, a valve configured to block the bypass hole (23), said valve being deformed and opening the bypass hole (23) when a pressure equal to a predetermined pressure was applied to the valve rank or exceed it.
4. A two-stage rotary compressor (100) according to any one of claims 1 to 3, in which, when the central axis of the drive shaft (5) is taken as the reference point, and the direction of rotation from the outlet (16) of the low pressure stage to the bypass mechanism with a shortened the distance is taken as the forward direction, the hole of the intermediate channel leading to the said outlet space of the low pressure stage is made downstream than the bypass mechanism, in the forward direction.
5. A two-stage rotary compressor (100) according to any one of claims 1 to 3, in which a pipe (61) is connected that injects refrigerant into said exhaust space of the low pressure stage.
6. A two-stage rotary compressor (100) according to any one of claims 1 to 3, in which the position of the refrigerant inlet of the compression chamber (15) of the low pressure stage and the position of the refrigerant inlet of the compression chamber (35) of the high pressure stage are essentially in one and the same phase.
7. Two-stage rotary compressor (100) according to any one of claims 1 to 3, in which, when the central axis of the drive shaft (5) is taken as the reference point, and the direction of rotation from the blade (26) of the low pressure stage to the inlet with a shortened distance is taken as the forward direction, the intermediate channel is made downstream than the inlet mentioned in the forward direction.
RU2012122456/06A 2011-07-28 2012-05-30 Double-staged rotary compressor RU2501978C1 (en)

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KR101376872B1 (en) 2014-03-20

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