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WO2018181977A1 - Machine à fluide à volutes - Google Patents

Machine à fluide à volutes Download PDF

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Publication number
WO2018181977A1
WO2018181977A1 PCT/JP2018/013817 JP2018013817W WO2018181977A1 WO 2018181977 A1 WO2018181977 A1 WO 2018181977A1 JP 2018013817 W JP2018013817 W JP 2018013817W WO 2018181977 A1 WO2018181977 A1 WO 2018181977A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
air
cooling
guide space
cooling air
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/013817
Other languages
English (en)
Japanese (ja)
Inventor
佐藤　徹
佳也 加藤
和秀 星
淳一 浅見
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Anest Iwata Corp
Original Assignee
Anest Iwata Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2017072642A external-priority patent/JP2018173053A/ja
Priority claimed from JP2017072639A external-priority patent/JP2018173050A/ja
Priority claimed from JP2017072640A external-priority patent/JP2018173051A/ja
Priority claimed from JP2017072641A external-priority patent/JP2018173052A/ja
Priority claimed from JP2017072638A external-priority patent/JP6928471B2/ja
Application filed by Anest Iwata Corp filed Critical Anest Iwata Corp
Priority to EP18778176.0A priority Critical patent/EP3604811B1/fr
Priority to CN201880022378.8A priority patent/CN110475972B/zh
Publication of WO2018181977A1 publication Critical patent/WO2018181977A1/fr
Priority to US16/583,877 priority patent/US20200018313A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C23/005—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 dissimilar 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
    • F04C23/001—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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation

Definitions

  • the present disclosure relates to a scroll fluid machine.
  • a fluid machine including a compressor that compresses a gas such as air is used in various fields of industry, and a scroll compressor is known as one method.
  • a scroll compressor typically, a compression chamber is formed between the fixed scroll and the orbiting scroll arranged to face each other, and the compression chamber is reduced while moving toward the center side with the rotation of the orbiting scroll. Pressurized gas is generated.
  • the pressure of the pressurized gas increases as the compression chamber approaches the center side, so that the temperature also increases.
  • Scroll compressors are provided with cooling means in order to suppress the temperature rise of the fixed scroll and the orbiting scroll.
  • cooling air is generated by a blower fan connected to a drive shaft for rotationally driving the orbiting scroll, and the cooling air is formed on the back side of the fixed scroll and the orbiting scroll via a duct.
  • the structure which cools a fixed scroll and a turning scroll by supplying to a radiation fin is disclosed.
  • At least one embodiment of the present invention has been made in view of the above-described circumstances, and an object thereof is to provide a scroll fluid machine capable of realizing good compression efficiency with a simple configuration.
  • Patent Document 1 an intermediate cooler for cooling the pressurized gas generated in the low-pressure side compression chamber is provided outside the compressor body.
  • an intermediate cooler for cooling the pressurized gas generated in the low-pressure side compression chamber is provided outside the compressor body.
  • At least one embodiment of the present invention has been made in view of the above circumstances, and includes an intermediate cooler disposed between the low-pressure side compression chamber and the high-pressure side compression chamber with a simple configuration, so that the installation space of the entire facility is increased. And it aims at providing the scroll fluid machine which can reduce manufacturing cost.
  • a check valve for preventing the backflow of the pressurized gas may be disposed downstream of the compression chamber.
  • the check valve used for such a purpose has a limited operating temperature range due to its structure, and cannot withstand the high-temperature discharge gas immediately after being discharged from the compression chamber. Therefore, in the conventional typical configuration, the high-temperature pressurized gas discharged from the compression chamber is cooled by an aftercooler, which is an external device installed on the downstream side, and then disposed so as to pass through the check valve. There was a need to do.
  • Such a configuration requires an aftercooler, a check valve, and the like to be disposed outside the scroll fluid machine, which increases the scale of the apparatus and increases installation space and manufacturing costs.
  • At least one embodiment of the present invention has been made in view of the above-described problems, and an object thereof is to provide a scroll fluid machine that can effectively suppress the temperature of discharged gas with a simple configuration.
  • the orbiting scroll is driven to rotate by torque from the drive shaft, so that distortion is likely to occur compared to a fixed scroll.
  • mechanical strength may be ensured by providing a reinforcing structure on the back side of the orbiting scroll.
  • a reinforcing structure for example, a rib-shaped reinforcing member extending in one direction is used on the back surface of the revolving end plate having a substantially disc shape.
  • such a rib-shaped reinforcing member has a convex shape that protrudes from the back of the revolving end plate to which the cooling air is supplied, and therefore hinders the flow of the cooling air and reduces the cooling performance of the orbiting scroll. There is a fear.
  • the rib-shaped reinforcing member can provide a relatively effective reinforcing effect in the vicinity where the reinforcing member is provided, but it is difficult to obtain a sufficient reinforcing effect in a region away from the reinforcing member, and the orbiting scroll can be used as a whole. Has not been able to be fully reinforced.
  • At least one embodiment of the present invention has been made in view of the above circumstances, and an object thereof is to provide a scroll fluid machine capable of improving the strength over a wide range while effectively suppressing the temperature rise of the orbiting scroll. To do.
  • a plurality of heat radiation fins provided on the fixed scroll and the orbiting scroll as cooling means for the fixed scroll and the orbiting scroll are typically provided at substantially equal intervals along the cooling air blowing direction. Therefore, the cooling air supplied to these radiating fins has a relatively good cooling action on the upstream side, but the temperature of the cooling air rises toward the downstream side, so the cooling action gradually weakens and the cooling action decreases. Resulting in. As a result, a difference in the degree of cooling occurs between the upstream side and the downstream side, which may cause a temperature difference on the fixed scroll and the orbiting scroll. Such a temperature difference becomes a factor causing distortion in the fixed scroll and the orbiting scroll.
  • At least one embodiment of the present invention has been made in view of the above-described circumstances, and an object thereof is to provide a scroll fluid machine that can obtain a uniform cooling action over a wide range of a fixed scroll or a turning scroll.
  • a scroll fluid machine is a compression chamber formed between a first scroll and a second scroll.
  • a compressor main body capable of compressing the introduced fluid
  • a cover that forms at least part of the compressor main body so as to form an air guide space
  • a cooling fan for supplying cooling air, and a part of the cooling air is configured to be supercharged to the intake port through the air guide space.
  • a part of the cooling air supplied from the blower fan to cool the first scroll and the second scroll forming the compression chamber is supplied to the intake port of the compressor body. Configured to be.
  • a part of the cooling air used for cooling the first scroll and the second scroll can be supercharged, so that the temperature rise of the first scroll and the second scroll can be achieved with a simple configuration.
  • a part of the cooling air for cooling the first scroll and the second scroll is supercharged to the intake port via the air guide space formed by the cover. Is done.
  • the dynamic pressure of the cooling air is converted to static pressure and is supercharged to the intake port. Therefore, even if there is a considerable variation in the amount of air blown from the blower fan, it is possible to stably supercharge the intake port.
  • the air guide space has a larger flow area than a duct for introducing outside air from the blower fan to the compressor body.
  • the static pressure can be generated satisfactorily from the dynamic pressure of the cooling air sent through the duct, and the air inlet is stable. Supercharging can be realized.
  • the cover has a curved inner wall so as to rectify the outside air introduced into the air guide space toward the intake port
  • the cover forming the inner wall of the air guide space is formed in a curved surface, so that the cooling air introduced into the air guide space is rectified toward the intake port. Thereby, the cooling air supplied to the air guide space is efficiently guided to the intake port, and good supercharging efficiency is obtained.
  • a filter is further provided for removing foreign matters contained in the outside air supercharged to the intake port.
  • the apparatus further includes a discharge pipe through which the pressurized gas discharged from the compression chamber flows, and the discharge pipe flows through the discharge pipe. Is provided so as to penetrate the air guide space so as to be cooled by the cooling air introduced into the air guide space.
  • the supercharging to the intake port is performed via the air guide space as described above.
  • the additional air discharged from the compression chamber is utilized using the air guide space.
  • Cooling of pressurized gas can also be used.
  • the pressurized gas generated in the compressor main body is discharged through a discharge pipe provided so as to penetrate the air guide space. Therefore, the pressurized gas flowing through the discharge pipe is cooled by the cooling air introduced into the air guide space. In this way, by cooling the pressurized gas flowing through the discharge pipe by the air guide space provided for supercharging the intake port, for example, an external device such as an aftercooler becomes unnecessary, the system scale is reduced, the installation space and Manufacturing costs can be saved effectively.
  • a check valve is built in the discharge pipe.
  • a check valve for preventing the backflow of the pressurized gas may be disposed downstream of the compression chamber. Since the check valve used for such an application has a limited operating temperature range due to its structure, it cannot withstand the high temperature discharged gas immediately after being discharged from the compression chamber. According to the configuration, since the temperature of the pressurized gas flowing through the discharge pipe can be suppressed as described above, a check valve for preventing backflow can be built in the discharge pipe.
  • a scroll fluid machine is formed by a housing and a fixed wrap fixed to the housing and erected on a fixed end plate.
  • a fixed scroll in which a spiral groove is closed by a partition partitioning the low-pressure side compression chamber and the high-pressure side compression chamber; and the housing is accommodated opposite to the fixed scroll, and together with the fixed scroll, the low-pressure side compression chamber and A part of the cooling air supplied to at least one of the fixed scroll and the orbiting scroll is formed between the orbiting scroll that forms the high-pressure side compression chamber and is rotatably supported by a drive shaft, and the fixed scroll.
  • a cover that forms a wind guide space that can be introduced, and pressurized gas discharged from the low-pressure side compression chamber are cooled in the wind guide space. It cooled by heat exchange with, and an intercooler that is configured to return the pressurized gas after cooling in the high pressure side compression chamber.
  • the spiral groove formed by the fixed wrap of the fixed scroll is partitioned by the partition wall, so that the low pressure side compression chamber and the high pressure side compression chamber are formed between the rotating scroll and the scroll. Is done.
  • the pressurized gas discharged from the low-pressure side compression chamber is cooled by the intermediate cooler and then returned to the high-pressure side compression chamber, so that the scroll fluid machine according to this configuration is configured as a multistage compressor.
  • the cover forms an air guide space into which a part of the cooling air supplied to at least one of the fixed scroll and the orbiting scroll can be introduced.
  • This air guide space constitutes an intermediate cooler that cools the pressurized gas discharged from the low-pressure side compression chamber.
  • the intercooler the high-temperature pressurized gas discharged from the low-pressure side compression chamber is cooled by heat exchange with the cooling air in the wind guide space, and the cooled pressurized gas is returned to the high-pressure side compression chamber.
  • an intermediate cooler capable of cooling using a part of the cooling air supplied to at least one of the fixed scroll and the orbiting scroll is configured integrally with the compressor body. Therefore, the configuration can be simplified as compared with the conventional case, and the installation space and manufacturing cost of the entire equipment can be effectively reduced.
  • the intermediate cooler connects a low-pressure side discharge port of the low-pressure side compression chamber and a high-pressure side suction port of the high-pressure side compression chamber. And a heat radiating pipe disposed in the air guide space.
  • the high-temperature pressurized gas discharged from the low-pressure side discharge port of the low-pressure side compression chamber passes through the heat radiating pipe disposed in the wind guide space. After being cooled by heat exchange with cooling air introduced into the high pressure side, it is supplied to the high pressure side suction port of the high pressure side compression chamber.
  • the heat radiating pipe is disposed so as to be folded back on the inner wall of the air guide space.
  • the heat radiating pipe in the configuration of the above (9), includes a plurality of folded portions in which a plurality of heat radiating portions extending along the cooling air are formed lower than the plurality of heat radiating portions. It is configured to be connected through a section.
  • a heat radiating pipe can arrange
  • the low-pressure side discharge port is disposed on the downstream side of the cooling air as compared with the high-pressure side suction port.
  • the low-pressure pressurized gas cooled by the intermediate cooler flows into the high-pressure side suction port. Compared to the downstream side of the cooling air.
  • the cooling air is heat-exchanged with the pressurized gas after being cooled by the intermediate cooler, so that the temperature rise is small and a relatively low temperature cooling air can be supplied to the downstream side.
  • the high-temperature pressurized gas before being cooled by the intermediate cooler on the downstream side can be effectively cooled.
  • the apparatus further includes a discharge pipe through which the pressurized gas discharged from the high-pressure side compression chamber flows, The pressurized gas flowing in the discharge pipe is provided so as to penetrate the air guide space so as to be cooled by the cooling air introduced into the air guide space.
  • a check valve is built in the discharge pipe.
  • a check valve for preventing the backflow of the pressurized gas may be disposed downstream of the compression chamber. Since the check valve used for such an application has a limited operating temperature range due to its structure, it cannot withstand the high-temperature discharge gas immediately after being discharged from the compression chamber. According to the configuration, since the temperature of the pressurized gas flowing through the discharge pipe can be suppressed as described above, a check valve for preventing backflow can be built in the discharge pipe.
  • a scroll fluid machine is a compressor capable of generating pressurized gas in a compression chamber formed by a fixed scroll and a turning scroll.
  • a cover that forms an air introduction space into which cooling air can be introduced between the main body and the compressor main body, and the compressor main body formed to discharge the pressurized gas generated in the compression chamber.
  • a discharge pipe connected to the discharge port and provided so as to penetrate the air guide space.
  • the pressurized gas generated in the compressor body is discharged from the discharge port to the outside through the discharge pipe. Since the discharge pipe is provided so as to penetrate the air guide space into which the cooling air is introduced, the high-temperature pressurized gas flowing through the discharge pipe is cooled by the cooling air introduced into the air guide space.
  • the wind guide space is configured by a cover provided so as to cover the compressor body, and the temperature of the discharge gas can be effectively suppressed with a simple configuration.
  • the discharge pipe in the configuration of (14), is configured such that the heat exchange part exposed to the air guide space has higher thermal conductivity than the surroundings. .
  • the discharge pipe through which the high-temperature pressurized gas flows has a high heat conductivity in the heat exchange part exposed to the wind guide space, so that the cooling wind introduced into the wind guide space Heat exchange is promoted, and the temperature of the discharged gas can be more effectively suppressed.
  • a cooling fin is provided on the outer surface of the discharge pipe.
  • the cooling fins on the outer surface of the discharge pipe, the heat exchange area with the cooling air introduced into the wind guide space can be increased, and the discharge gas can be more effectively discharged. Temperature can be suppressed. It is also possible to reinforce the mechanical strength of the discharge pipe through which high-pressure pressurized gas flows.
  • the cooling fin extends along a flow direction of the cooling air introduced into the wind guide space.
  • the cooling fins formed on the outer surface of the discharge pipe extend along the flow direction of the cooling air, and thus do not hinder the flow of the cooling air. As a result, heat exchange between the discharge gas and the cooling air is promoted, and the temperature of the discharge gas can be more effectively suppressed.
  • a check valve is built in the discharge pipe.
  • the compression chamber in any one of the configurations (14) to (18), includes a low-pressure side compression chamber and a high-pressure side compression chamber that are partitioned by a partition wall.
  • the compression chamber is compressed in multiple stages so that the high temperature
  • the pressurized gas can be cooled effectively.
  • a scroll fluid machine has a fixed scroll having a fixed end plate and a fixed wrap provided on the fixed end plate, An orbiting scroll provided on a first surface of the end plate and the fixed end plate, and a orbiting scroll that forms a compression chamber together with the fixed scroll, wherein the orbiting end plate is opposite to the first surface
  • the second surface to which cooling air is supplied has a convex shape that continuously rises, and the convex shape coincides with the orbiting center in which the center of gravity of the orbiting scroll is eccentric from the center of the orbiting end plate Formed as follows.
  • the second surface of the orbiting end plate constituting the orbiting scroll has a convex shape.
  • the thickness of the orbiting end plate is increased, and the mechanical strength of the orbiting scroll is improved.
  • the convex shape which the 2nd surface has is formed so that it may rise continuously, it does not disturb the cooling air supplied in order to cool a turning scroll. As a result, a good cooling effect is obtained with the orbiting scroll, and the occurrence of distortion can be effectively suppressed.
  • the convex shape is formed over a region including the center of the turning end plate.
  • a plurality of heat radiation fins extending along the blowing direction of the cooling air are formed on the second surface.
  • the cooling performance of the orbiting scroll can be further improved, and the strength of the orbiting scroll can be further improved.
  • the convex shape is provided on the second surface of the orbiting end plate.
  • the plurality of heat radiating fins are arranged on the second surface so as to become denser as the thickness of the swivel end plate increases.
  • the plurality of radiating fins provided on the second surface are arranged more densely in a region where the thickness of the swivel end plate is larger.
  • the first surface has a concave thinning portion in a non-contact region that does not contact the fixed scroll.
  • the compression chamber includes a low-pressure side compression chamber and a high-pressure side compression chamber that are partitioned by a partition wall.
  • the compression chamber is configured as a multistage fluid machine including a low-pressure side compression chamber and a high-pressure side compression chamber partitioned by a partition wall.
  • the pressurized gas temperature in the high-pressure side compression chamber is particularly high. Therefore, by adopting the above-described configuration, it is possible to realize a scroll fluid machine that is less likely to be distorted by ensuring the strength over a wide range while effectively suppressing the temperature rise of the orbiting scroll.
  • a scroll fluid machine has a fixed scroll provided with a fixed wrap on the fixed end plate, and a turning lap on the turning end plate. And a orbiting scroll that forms a compression chamber together with the fixed scroll, and at least one of the fixed end plate and the orbiting end plate has the first surface provided with the fixed wrap or the orbiting wrap, A second surface provided with a plurality of radiating fins located on the opposite side of the first surface and extending along cooling air introduced from the blower fan, the plurality of radiating fins, It is arranged more densely on the downstream side of the cooling air than on the upstream side.
  • the plurality of radiating fins are provided on the back side (second surface) where the wrapping of the fixed end plate or the swiveling end plate is not provided. Since these radiating fins are arranged more densely on the downstream side of the cooling air than on the upstream side, the flow velocity of the cooling air gradually increases from the upstream side toward the downstream side. Therefore, the cooling effect on the downstream side where the temperature of the cooling air becomes high is improved, and the temperature difference generated between the upstream side and the upstream side can be suppressed. In this way, a uniform cooling action can be obtained over a wide range of fixed scrolls or orbiting scrolls.
  • the plurality of radiating fins are arranged such that a pitch distance between adjacent radiating fins is larger on the upstream side of the cooling air than on the downstream side.
  • a plurality of cooling fins can be arranged more densely on the downstream side of the cooling air than on the upstream side.
  • the compression chamber moves gas toward the center side when the fixed scroll and the orbiting scroll are driven to rotate relative to each other.
  • the cooling fins are configured to be compressible, and at least one of the fixed end plate and the swivel end plate is arranged more sparsely on the center side than the outer peripheral side.
  • the compression chamber formed by the fixed scroll and the orbiting scroll compresses the gas toward the center side, so that the temperature of the fixed scroll and the orbiting scroll is likely to rise toward the center side. Therefore, the cooling according to heat load distribution is attained by arrange
  • the turning end plate has a convex shape in which the second surface continuously rises, and the plurality of radiating fins are On the second surface, the swivel end plates are arranged so as to become denser as the thickness thereof increases.
  • the fixed scroll and the orbiting scroll are configured such that the cooling air is introduced from the blower fan through a duct. Has been.
  • the cooling air supplied to the fixed scroll and the orbiting scroll is introduced from the blower fan through the duct having a predetermined length. For this reason, the cooling air is weakened not only by pressure loss generated in the duct, but in this configuration, by having a plurality of cooling fins arranged as described above, a good cooling effect can be obtained even if the cooling air is weakened. can get.
  • a scroll fluid machine capable of realizing good compression efficiency with a simple configuration can be provided.
  • a scroll capable of reducing the installation space and manufacturing cost of the entire equipment by providing an intermediate cooler arranged between the low pressure side compression chamber and the high pressure side compression chamber with a simple configuration.
  • a fluid machine can be provided.
  • a scroll fluid machine capable of obtaining a uniform cooling action over a wide range of a fixed scroll or a turning scroll.
  • FIG. 1 It is a perspective view showing the appearance of the scroll compressor concerning at least one embodiment of the present invention. It is a vertical sectional view which passes along the drive shaft of the scroll compressor of FIG. It is a horizontal sectional view which passes along the drive shaft of the scroll compressor of FIG. It is a top view which shows the turning scroll with which the compressor main body of FIG. 1 is provided from the 1st surface side. It is a top view which shows the turning scroll of FIG. 4 from the 2nd surface side. It is a comparative example of FIG. It is another modification of FIG. It is a top view which shows the fixed scroll with which the compressor main body of FIG. 1 is provided from the 2nd surface side. It is sectional drawing which passes along the central axis of the turning scroll of FIG.
  • FIG. 5 It is sectional drawing which passes along the central axis of the turning scroll of FIG. 5 is a contour line distribution on the second surface of the orbiting scroll of FIG. It is a modification of FIG. It is a modification of FIG. It is another modification of FIG. It is a schematic diagram which shows the cooling fin provided in the outer surface of the discharge pipe in FIG. 14 from the inner side of a cover. It is a top view which shows the fixed scroll and turning scroll in a single winding two-stage type scroll compressor. It is a perspective view which shows the state which removed the cover in the scroll compressor which concerns on this embodiment. It is a vertical sectional view which passes along a drive shaft in the state where a cover was attached to the scroll compressor of FIG. It is a vertical sectional view of a supercharged scroll compressor.
  • expressions representing shapes such as quadrangular shapes and cylindrical shapes not only represent shapes such as quadrangular shapes and cylindrical shapes in a strict geometric sense, but also within the range where the same effect can be obtained. A shape including a chamfered portion or the like is also expressed.
  • the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one constituent element are not exclusive expressions for excluding the existence of the other constituent elements.
  • FIG. 1 is a perspective view showing an appearance of a scroll compressor 1 according to at least one embodiment of a scroll fluid machine according to the present invention
  • FIG. 2 is a vertical sectional view passing through a drive shaft 22 of the scroll compressor 1 of FIG.
  • FIG. 3 is a horizontal sectional view passing through the drive shaft 22 of the scroll compressor 1 of FIG.
  • the left side in FIGS. 2 and 3 is referred to as the front, and the right side is referred to as the rear.
  • the scroll compressor 1 is a compressor for compressing a gas such as air.
  • the scroll compressor 1 sucks and purifies a gas to be compressed, and compresses the gas purified by the filter unit 2.
  • a compressor main body 4 a power transmission unit 6 for transmitting power from a power source (not shown) to each part of the scroll compressor 1, a blower unit 8 for blowing cooling air of the scroll compressor 1, Is provided.
  • the filter unit 2 is disposed at the upper front portion of the scroll compressor 1, and the compressor body 4, the power transmission unit 6, and the blower unit 8 are sequentially disposed from the front side behind the filter unit 2.
  • the filter unit 2 has a hollow filter casing 10 as a casing.
  • the filter casing 10 includes a cylindrical portion 10a having a substantially cylindrical shape, and an inclined portion 10b inclined toward the outer surface of the compressor body 4 at the rear of the cylindrical portion 10a.
  • the inlet 12 for sucking in the gas used as compression object from the outside is provided in the upper surface of the inclination part 10b among the filter casings 10.
  • FIG. The air inlet 12 is formed in a plurality of slits extending in parallel to each other in the left-right direction. Note that the intake port 12 is not necessarily provided. In that case, the gas to be compressed is supplied from the blower fan 52 (see below).
  • a filter element 14 for removing foreign matters such as dust and dust contained in the gas sucked from the air inlet 12 is disposed.
  • the gas introduced from the air inlet 12 passes through the filter element 14 to be purified, and is supplied to the compressor body 4 located on the downstream side.
  • the compressor body 4 includes a compressor housing 16.
  • the compressor housing 16 is formed of, for example, an aluminum alloy.
  • a front upper portion of the compressor housing 16 is connected to the filter unit 2 described above, and is configured such that the gas that has passed through the filter element 14 is introduced into the compressor body 4 through the introduction path 15. Yes.
  • the rear side of the compressor housing 16 is connected to a bearing case 42 constituting the power transmission unit 6 by a plurality of bolts (not shown).
  • a fixed scroll 18 which is an example of a first scroll and a turning scroll 20 which is an example of a second scroll are accommodated.
  • the fixed scroll 18 is fixed to the compressor housing 16, and the orbiting scroll 20 is disposed in the compressor housing 16 so as to face the fixed scroll 18.
  • the orbiting scroll 20 is pivotally supported by an eccentric shaft portion 23 provided at the tip of the drive shaft 22 and is rotationally driven by the power transmitted from the power transmission unit 6.
  • the fixed scroll 18 includes a substantially disc-shaped fixed end plate 19.
  • a spiral fixed wrap 21 is erected on the first surface of the fixed end plate 19 facing the orbiting scroll 20.
  • a heat radiation fin 24 for heat radiation is provided on the second surface of the fixed end plate 19 opposite to the first surface. As will be described later, the cooling fins sent from the blower unit 8 are supplied to the radiating fins 24 to cool the fixed scroll 18.
  • the orbiting scroll 20 includes a substantially disc-shaped orbiting end plate 26.
  • a spiral orbiting wrap 28 is erected on the first surface of the orbiting end plate 26 facing the fixed scroll 18.
  • a heat radiating fin 30 is provided on the second surface of the swivel end plate 26 opposite to the first surface. As will be described later, cooling air supplied from the blower unit 8 is introduced into the heat radiation fin 30 to cool the fixed scroll 18.
  • the scroll compressor 1 is a so-called asymmetric wrap scroll compressor.
  • the present invention is not limited to the asymmetric wrap scroll compressor, and may be a so-called symmetric wrap scroll compressor in which the length of the fixed wrap 21 and the length of the orbiting wrap 28 are the same.
  • a revolving plate 32 having a substantially disc shape is fixed to the rear side of the orbiting scroll 20 in a state of being directly connected to the eccentric shaft portion 23 of the drive shaft 22.
  • a bearing portion 37 is formed integrally with the swivel plate 32.
  • a rotary bearing 33 for rotatably supporting the eccentric shaft portion 23 provided at the tip of the drive shaft 22 is disposed in the bearing portion 37.
  • a plurality of rotation preventing mechanisms 34 for revolving while preventing the revolving motion of the orbiting scroll 20 are provided along the circumferential direction of the revolving plate 32, that is, the orbiting scroll 20. They are provided at substantially equal intervals.
  • the orbiting scroll 20 When the drive shaft 22 is rotationally driven by the power from the power transmission unit 6, the orbiting scroll 20 performs a revolving motion, and accordingly, the volume of the compression chamber 36 formed between the fixed scroll 18 and the orbiting scroll 20 is increased.
  • the pressure gradually decreases from the outer peripheral side toward the inner peripheral side, and suction and compression are performed.
  • the compression chamber 36 is formed in a substantially crescent shape by being partitioned by the fixed wrap 21 and the swirl wrap 28. Thereby, the gas introduced into the compressor main body 4 from the introduction path 15 is gradually compressed toward the inner peripheral side.
  • the pressurized gas generated in the compression chamber 36 is discharged from a discharge port 38 provided at the center of the fixed scroll 18.
  • a flat lid portion 53 is fixed in front of the compressor housing 16.
  • the lid 53 is further covered with a cover 63 from the front, and an air guide space 57 into which a part of the cooling air from the blower unit 8 can be introduced is formed between the lid 53 and the cover 63.
  • a discharge plug 67 connected to an external pressurized gas supply destination is provided on the outer surface of the cover 63.
  • the discharge plug 67 is connected to a discharge port 38 provided at the center of the fixed scroll 18 through a discharge pipe 59 disposed so as to penetrate the air guide space 57 inside the cover 63. .
  • the pressurized gas generated in the compression chamber 36 is discharged from the discharge port 38 to the outside through the discharge pipe 59.
  • the power transmission unit 6 is a unit having a function of transmitting power supplied from an external power source (not shown) to each part of the scroll compressor 1.
  • the power transmission unit 6 has a driven pulley 40 that can input power from an external power source at the rear end portion of the drive shaft 22 projecting rearward of the blower unit 8.
  • the driven pulley 40 has, for example, an endless transmission in which a lower portion is wound around a main driving pulley (not shown) fixed to an output shaft of a power source such as an electric motor or an engine installed below the scroll compressor 1. By rotating the upper part of a belt (not shown), the rotation of the power source is transmitted to the drive shaft 22.
  • the power input to the driven pulley 40 rotates the drive shaft 22 and is transmitted to each part of the scroll compressor 1 such as the compressor body 4 and the blower unit 8.
  • bearing case 42 constituting the casing of the power transmission unit 6 is formed of, for example, a casting having a higher strength than the compressor housing 16.
  • Ball bearings 44 and 46 are provided in the bearing case 42 so as to be spaced apart from each other by a predetermined amount in the front-rear direction, and the drive shaft 22 is rotatably supported.
  • the eccentric shaft portion 23 described above is provided on the front end side of the drive shaft 22. Further, as shown in FIG. 2, a balance weight 48 for adjusting the balance on the orbiting scroll 20 side is provided on the outer periphery of the front portion of the eccentric shaft portion 23.
  • the blower unit 8 includes a blower fan 52 accommodated in a fan casing 50.
  • the blower fan 52 is connected to the drive shaft 22 and is configured to be rotationally driven by the power transmitted from the power transmission unit 6.
  • the blower fan 52 is, for example, a sirocco fan.
  • the blower unit 8 When the blower fan 52 is driven, the blower unit 8 sucks outside air (air) from the opening 55 provided in front of the fan casing 50, and the outside air is pumped toward the duct 54 provided on the downstream side of the blower fan 52.
  • the duct 54 is a tubular member having a substantially cylindrical shape. As shown in FIG. 3, the duct 54 bypasses the side of the power transmission unit 6 from the side of the fan casing 50 and is lateral to the compressor body 4. It is configured to be connected from. Thereby, the outside air sent from the blower unit 8 to the duct 54 is supplied to the compressor body 4 as cooling air.
  • the cooling air introduced from the duct 54 to the compressor main body 4 inside the compressor housing 16 has a first air passage 56, a second air passage 58, and a third air blow.
  • Each branch is branched into a passage 60.
  • the first air passage 56 is a passage for supplying cooling air to the radiating fins 30 provided on the second surface side of the orbiting end plate 26, and mainly cools the orbiting scroll 20.
  • the second air passage 58 is a passage for supplying cooling air to the radiation fins 24 provided on the second surface side of the fixed end plate 19, and mainly cools the fixed scroll 18.
  • the third air passage 60 is a passage for supplying cooling air to the air guide space 57 provided in front of the compressor housing 16.
  • FIG. 4 is a plan view showing the orbiting scroll 20 provided in the compressor main body 4 of FIG. 1 from the first surface side
  • FIG. 5 is a plan view showing the orbiting scroll 20 of FIG. 4 from the second surface side.
  • a spiral orbiting wrap 28 is erected on the orbiting end plate 26 on the first surface side of the orbiting scroll 20.
  • a groove 61 is formed at the tip of the orbiting wrap 28 along the length direction of the orbiting wrap 28 so that a chip seal (not shown) for sealing a gap with the fixed scroll 18 can be mated. Yes.
  • a plurality of radiating fins 30 are erected on the orbiting end plate 26. Cooling air is introduced into the plurality of heat radiation fins 30 from the duct 54 via the first air passage 56 (see FIG. 3).
  • the plurality of radiating fins 30 provided on the swivel end plate 26 have a substantially straight shape, and extend substantially in parallel along the flow direction of the cooling air introduced from the first air passage 56. Yes.
  • FIG. 6 is a comparative example of FIG.
  • the plurality of heat radiating fins 30 ′ provided on the turning end plate 26 ′ have a non-straight shape (wave shape) curved in a wave shape.
  • the heat dissipating fin 30 ′ having such a non-straight shape turbulent flow is generated along a wave-shaped curve or the airflow resistance is increased.
  • the heat radiation fin 30 having a substantially straight shape as shown in FIG. 5 the flow of the cooling air from the first air passage 56 is not hindered, and the heat with the heat radiation fin 30. Since the exchange rate can be improved, good cooling performance can be obtained.
  • the cooling air introduced into the heat radiating fin 30 is supplied from the blower fan 52 at a position separated via the duct 54 having a predetermined length, the heat radiating fin 30 is in a state where the wind force is reduced to some extent due to pressure loss.
  • the radiating fins 30 have a substantially straight shape as described above, even if the cooling wind is weakened in this way, good heat exchange is possible, and an excellent cooling action is obtained. It is done.
  • an electric motor may be incorporated as a power source integrally with the power transmission unit 6.
  • the duct 54 becomes longer as the power transmission unit 6 becomes larger. End up. When the duct 54 is lengthened in this way, the cooling air passing through the duct 54 is easily affected by pressure loss, but a good cooling effect can be ensured by the above action.
  • a plurality of conventional heat dissipating fins 30 ' are typically provided at substantially equal intervals along the air blowing direction of the cooling air. Therefore, the cooling air introduced from the first air passage 56 can obtain a relatively good cooling action on the upstream side of the radiating fin 30 ′, but the cooling air temperature gradually rises on the downstream side and the cooling action is increased. It will decline. As a result, such a deviation in cooling action causes a temperature difference on the orbiting scroll 20 and causes distortion.
  • the plurality of radiating fins 30 are arranged closer to the upstream side on the downstream side of the cooling air.
  • the plurality of radiating fins 30 are configured such that the pitch distance between adjacent radiating fins 30 is larger on the upstream side of the cooling air than on the downstream side.
  • the pitch distance L1 on the upstream side is configured to be larger than the pitch distance L2 on the downstream side. Therefore, the cooling air introduced from the first air passage 56 increases in the wind speed toward the downstream side (that is, the downstream flow velocity V2 becomes larger than the upstream flow velocity V1), and the upstream and downstream sides.
  • the bias of the cooling action between the sides can be reduced.
  • the orbiting scroll 20 can be uniformly cooled, and distortion of the orbiting scroll 20 can be effectively suppressed.
  • the plurality of heat radiation fins 30 may be configured to be denser on the downstream side of the cooling air than on the upstream side by making the downstream side thicker than the upstream side of the cooling air. Also in this case, as in FIG. 5, the gap between the heat radiating fins 30 becomes narrower toward the downstream side, so that the flow velocity of the cooling air increases toward the downstream side, and the same effect as described above can be obtained.
  • FIG. 7 shows another modification of FIG.
  • the plurality of heat radiating fins 30 may be arranged so as to be sparser on the center side than the outer peripheral side of the orbiting scroll 20.
  • the temperature of the pressurized gas in the compression chamber 36 becomes higher as the compression chamber 36 approaches the central portion.
  • the heat dissipating fins 30 sparsely toward the inner side, the inner side (that is, Since more cooling air can be taken into the center side), a higher cooling effect is obtained on the inner side where the temperature is likely to rise.
  • cooling according to the heat load distribution of the orbiting scroll 20 can be performed, and the occurrence of distortion in the orbiting scroll 20 can be more effectively suppressed.
  • the same idea can be applied to the heat dissipating fins 24 in the fixed scroll 18.
  • Cooling air is introduced into the radiating fins 24 in the fixed scroll 18 through the second air passage 58.
  • substantially straight radiating fins 24 extending substantially parallel to each other along the cooling air are arranged.
  • These radiating fins 24 are arranged so as to be denser from the upstream side at the downstream side of the cooling air supplied from the second air passage 58 and sparser from the outer peripheral side at the center side.
  • Each modification similar to the fin 30 is applicable.
  • FIG. 9 is a cross-sectional view passing through the central axis of the orbiting scroll 20 ′ of FIG. 6 (comparative example).
  • the reinforcing rib 70 is provided on the orbiting end plate 26 having a uniform thickness.
  • the reinforcing rib 70 is formed so as to extend along a direction substantially perpendicular to the radiating fin 30 through the center portion of the turning end plate 26 on the second surface on which the radiating fin 30 is provided.
  • the reinforcing rib 70 exhibits a relatively effective reinforcing effect in the vicinity of the reinforcing rib 70, but it is difficult to obtain a sufficient reinforcing effect in a region away from the reinforcing rib 70. Overall it has not been able to be fully reinforced. Further, as shown in FIG. 9, the reinforcing rib 70 has a shape protruding in a convex shape on the second surface, so that the cooling air from the first air passage 56 collides from the side surface side of the reinforcing rib 70 to cool the cooling rib. There is a possibility that the flow of the wind is obstructed and the cooling performance of the orbiting scroll 20 is deteriorated.
  • the turning end plate 26 has a convex shape 80 in which the second surface continuously rises.
  • 10 is a cross-sectional view passing through the central axis of the orbiting scroll 20 of FIG. 4, and FIG. 11 is a contour distribution of the orbiting end plate 26 on the second surface of the orbiting scroll 20.
  • the swivel end plate 26 has a non-uniform thickness so that the height increases with the top 81 as the center, and has a gentle mountain-shaped cross-sectional shape. Accordingly, the thickness of the orbiting scroll 20 is increased and the strength is improved as compared with the orbiting end plate 26 having a uniform thickness as in the conventional case (see FIG. 9).
  • the convex shape 80 on the turning end plate 26 is formed so that the center of gravity 82 of the turning scroll 20 coincides with the turning center eccentric from the center O of the turning end plate 26, as shown in FIG. Specifically, in the example of FIG. 11, the top 81 of the convex shape 80 is eccentric to the upper left from the center O of the turning end plate 26, and as a result, the center of gravity 82 is also formed to be eccentric from the center O. Yes.
  • the orbiting scroll 20 is eccentrically rotated, a process for adding a balance to the orbiting scroll 20 in order to finely adjust the orbiting scroll 20 has been performed. However, this has been a factor in complicating the apparatus configuration and increasing the work load.
  • the position of the center of gravity 82 of the orbiting scroll 20 can be arbitrarily adjusted by forming the convex shape 80 on the second surface, such a problem can be solved with a simple configuration. .
  • the convex shape 80 on the second surface of the turning end plate 26 may be formed over a region including the center O.
  • the inclination of the convex shape 80 becomes gentle. As a result, it becomes easier for the cooling air to pass through and good cooling performance can be exhibited.
  • a plurality of heat radiating fins 30 extending along the cooling air blowing direction are formed on the second surface having such a convex shape 80, as described above.
  • the convex shape 80 is provided on the second surface of the orbiting end plate 26, so that the thickness increases, so that the heat capacity also increases.
  • the orbiting scroll 20 having a large heat capacity can be effectively cooled.
  • the strength of the orbiting scroll 20 can be further improved by providing the radiation fins 30.
  • the arrangement of the plurality of radiating fins 30 on the second surface is as described above with reference to FIGS. 5, 6, and 7.
  • position so that it may become dense as the thickness of the turning end plate 26 becomes large on the surface. That is, in the swivel end plate 26 having the convex shape 80, the arrangement density of the radiation fins 30 increases as the thickness increases. Thereby, the amount of cooling can be distributed according to the heat capacity per unit area, uniform cooling over a wide area of the orbiting scroll 20 is possible, and distortion of the orbiting scroll 20 can be more effectively suppressed.
  • the first surface of the orbiting scroll 20 may have a concave thinning portion 92 in at least a part of the non-contact area 90 that does not contact the fixed scroll 18.
  • FIG. 12 is a modification of FIG.
  • the first surface side of the orbiting scroll 20 is disposed to face the fixed scroll 18 and forms a compression chamber 36 together with the fixed scroll 18.
  • This non-contact area 90 is at least the outer periphery of the first surface of the orbiting end plate 26 of the orbiting scroll 20 from the outermost orbiting wrap 28 (the portion of the orbiting wrap 28 corresponding to one turn from the outermost end).
  • This is the side area. 12 illustrates the case where the entire non-contact region 90 is formed as a concave thinning portion 92, but a part of the non-contact region 90 is partially formed as a concave thinning portion 92. Also good.
  • the thinning portion 92 may be provided on the first surface of the orbiting scroll 20, the thinning portion 92 may be formed on the first surface of the fixed scroll 18. In this case, since the fixed scroll 18 is fixed with respect to the compressor housing 16, the effect of balance adjustment cannot be obtained. There is an advantage that it can contribute to the increase of 36 capacity.
  • the discharge pipe 59 is configured to come into contact with the cooling air flowing through the air guide space 57 from the outside, and the high-temperature pressurized gas flowing through the discharge pipe 59 exchanges heat with the cooling air introduced into the air guide space 57. Is cooled by. Conventionally, the high-temperature pressurized gas discharged from the compressor body 4 has been supplied to the customer after being cooled by an aftercooler prepared outside, but in the present embodiment, the wind guide space is thus provided. Since the pressurized gas can be cooled at 57, an external device such as an aftercooler is unnecessary, which is advantageous for making the entire system compact.
  • the heat exchange part 59a exposed to the air guide space 57 in the discharge pipe 59 may be configured to have a higher thermal conductivity than the surroundings.
  • the heat exchanging portion 59a may be partially formed of a material having high thermoelectricity (for example, aluminum) or may be partially formed with a small tube thickness.
  • the discharge pipe 59 through which the high-temperature pressurized gas from the compressor body 4 flows is introduced into the wind guide space 57 because the heat exchanging portion 59a exposed to the wind guide space 57 has high thermal conductivity. This facilitates heat exchange with the cooling air to cool the discharged gas more effectively.
  • FIG. 13 is a modification of FIG.
  • a part of the discharge pipe 59 has an enlarged diameter portion 97 having an enlarged diameter, and a check valve 98 for preventing a backflow of the discharge gas is incorporated in the enlarged diameter portion 97.
  • a check valve 98 for preventing a backflow of the discharge gas is incorporated in the enlarged diameter portion 97.
  • this type of scroll compressor 1 when the compression operation is stopped, a phenomenon occurs in which the pressurized gas remaining in the discharge pipe 59 temporarily flows back toward the compressor body 4.
  • a configuration in which a check valve is conventionally provided on the downstream side of the discharge port 38 has been used, but this type of check valve has a limited operating temperature range. The high-temperature pressurized gas discharged from the discharge port 38 could not be withstood.
  • FIG. 14 is another modification of FIG. 2, and FIG. 15 is a schematic view showing the cooling fin 95 provided on the outer surface of the discharge pipe 59 from the inside of the cover 63 in FIG.
  • cooling fins 95 are provided on the outer surface of the discharge pipe 59.
  • the cooling fin 95 extends along the flow direction (left-right direction) of the cooling air introduced into the air guide space 57 via the third air passage 60. It is configured not to obstruct the flow. As a result, heat exchange between the discharge gas and the cooling air is promoted, and the temperature of the discharge gas can be more effectively suppressed.
  • the scroll compressor 1 that performs gas compression in a single stage has been described.
  • the scroll compressor 1 may be configured as a multistage compressor that performs gas compression over a plurality of stages.
  • the scroll compressor 1 is configured as a single-winding two-stage scroll compressor will be described.
  • FIG. 16 is a plan view showing the fixed scroll 18 and the orbiting scroll 20 in the single-winding two-stage scroll compressor 1.
  • 102 is provided. That is, the partition wall 102 is formed in a boss shape on the fixed end plate 19 so that the spiral groove formed by the fixed wrap 21 is closed in the middle.
  • the compression chamber 36 is partitioned into a low pressure side compression chamber 36a and a high pressure side compression chamber 36b.
  • the partition wall 102 may be formed integrally with the fixed end plate 19 or may be formed as a separate member.
  • a low pressure side discharge port 104 and a high pressure side suction port 106 are provided on both sides of the partition wall 102 in the spiral groove 100 (that is, inside the low pressure side compression chamber 36a and outside the high pressure side compression chamber 36b), respectively. ing.
  • the low pressure side discharge port 104 and the high pressure side suction port 106 are formed so as to penetrate the fixed end plate 19 substantially parallel to the central axis of the fixed scroll 18.
  • the low-pressure side compression chamber 36a is located on the outer side compared to the high-pressure side compression chamber 36b, and a gas (outside air) to be compressed is introduced from the introduction path 15.
  • the pressurized gas pressurized in the low pressure side compression chamber 36a is discharged from the low pressure side discharge port 104, cooled by an intermediate cooler 110 described later, and then introduced into the high pressure side suction port 106 of the high pressure side compression chamber 36b. .
  • the pressurized gas cooled by the intermediate cooler 110 is further compressed, and the pressurized gas is finally discharged from the discharge port 38 provided on the center side of the fixed end plate 19.
  • FIG. 17 is a perspective view showing a state in which the cover 63 is removed from the scroll compressor 1 according to this embodiment
  • FIG. 18 shows the drive shaft 22 in a state in which the cover 63 is attached to the scroll compressor 1 in FIG. FIG.
  • the scroll compressor 1 includes an intermediate cooler 110 configured to cool the pressurized gas discharged from the low-pressure side compression chamber 36a and return the cooled pressurized gas to the high-pressure side compression chamber 36b.
  • the intermediate cooler 110 is air-cooled, and includes an air guide space 57 into which cooling air is introduced, and a heat radiation pipe 112 that is disposed inside the air guide space 57 and through which the pressurized gas discharged from the low-pressure side compression chamber 36a flows. .
  • the air guide space 57 is formed by the cover portion 53 fixed to the fixed scroll and the cover 63 covering the cover portion 53, and the air guide space 57 is provided via the third air passage 60. Cooling air is introduced.
  • a heat radiating pipe 112 that connects the low pressure side discharge port 104 of the low pressure side compression chamber 36a and the high pressure side suction port 106 of the high pressure side compression chamber 36b is disposed on the lid 53 of the inner wall of the air guide space 57. .
  • the heat radiating pipe 112 flows through the heat radiating pipe 112 by being exposed to cooling air introduced from the third air passage 60 through the opening 100 formed in the vicinity of the edge of the lid portion 53 in the air guide space 57.
  • the hot pressurized gas is cooled.
  • the intermediate cooler 110 for cooling the pressurized gas using the cooling air introduced into the air guide space 57 can be configured integrally with the compressor body 4. Such a configuration is simpler than conventional ones, and can effectively reduce the installation space and manufacturing cost of the entire equipment.
  • the heat radiating tube 112 is formed of a metal material having excellent thermal conductivity such as aluminum. Further, the heat radiating tube 112 is provided on the lid 53 in a convex shape, and is configured such that the contact area with the cooling air introduced into the air guide space 57 is increased.
  • the heat radiating tube 112 is disposed on the lid 53 so as to be folded back in a predetermined pattern. Since the heat radiating pipe 112 has such a folded shape, a wide contact area with the cooling air introduced into the air guide space 57 can be secured, and a good cooling action can be obtained.
  • the heat radiating pipe 112 has a plurality of heat radiating portions 113 extending along the cooling air introduced from the third air passage 60 and lower than the plurality of heat radiating portions 113. It has a shape connected via a plurality of formed folded portions 114. Since the heat radiating pipe 112 has such a folded shape, the long heat radiating pipe 112 can be compactly arranged in a limited space on the lid portion 53. Further, since the plurality of heat radiating portions 113 extend along the blowing direction, the flow of the cooling air is not hindered, and the folded portion 114 is formed lower than the heat radiating portion 113, so that the outside air is adjacent between the heat radiating portions 113. It has been introduced smoothly. In this way, the cooling pipe 112 can provide a good cooling action.
  • the low-pressure side discharge port 104 is disposed on the downstream side of the cooling air on the lid portion 53 constituting the inner wall of the air guide space 57 as compared with the high-pressure side suction port 106. Then, as indicated by the broken line in FIG. 17, the flow path of the pressurized gas in the heat radiating pipe 112 passes from the low pressure side discharge port 104 to the downstream side of the central portion of the lid portion 53 and surrounds the central portion. Thus, it is configured to bypass the upstream side and be connected to the high-pressure side suction port 106. As a result, the pressurized gas flowing through the heat radiating pipe 112 flows from the downstream side toward the upstream side as indicated by arrows in FIG.
  • the temperature of the pressurized gas flowing through the heat radiating pipe 112 is lower on the upstream side of the cooling air than on the downstream side. Therefore, on the upstream side, the cooling air exchanges heat with the relatively low temperature pressurized gas, and the cooling air having a low temperature can be supplied to the downstream side heat radiation pipe 112 through which the relatively high temperature pressurized gas flows. Thereby, a good cooling action can be obtained over the entire heat radiating tube 112.
  • the air guide space 57 constituting the intermediate cooler 110 may be used for cooling the pressurized gas passing through the discharge pipe 59 as in the above-described embodiment.
  • an external device such as an aftercooler becomes unnecessary, and the system scale is reduced. And can save installation space and manufacturing cost effectively.
  • the heat radiating pipe 112 is arranged closer to the downstream side than the upstream side with respect to the cooling air introduced through the third air passage 60 following the heat radiating fin 30 described above with reference to FIG. Also good.
  • the flow area of the cooling air introduced into the heat radiating pipe 112 decreases from the upstream side toward the downstream side, the flow velocity becomes faster toward the downstream side where the temperature of the cooling air becomes higher.
  • a uniform cooling effect can be obtained in the entire heat radiating tube 112.
  • FIG. 19 is a vertical sectional view of the supercharged scroll compressor 1. Note that FIG. 19 is a modification of FIG. 2, and corresponding components are denoted by common reference numerals, and redundant description is omitted as appropriate.
  • the gas to be compressed is sucked from the opening 55 of the blower unit 8. That is, in the present embodiment, a part of the outside air sucked from the blower unit 8 becomes a gas to be compressed, and the rest is used as cooling air for the compressor body 4.
  • the inlet 12 of the filter unit 2 shown in FIG. 2 is sealed in this embodiment.
  • the scroll compressor 1 when the blower fan 52 is driven by the drive shaft 22, outside air is sucked from the opening 55 of the blower unit 8.
  • the outside air taken in from the opening 55 is sent to the compressor body 4 through a duct 54 connected to the side of the blower unit 8.
  • the duct 54 is connected to the side of the compressor body 4 and branches into a first air passage 56, a second air passage 58, and a third air passage 60, as in the above-described embodiment.
  • the outside air introduced into the first air passage 56 and the second air passage 58 is supplied to the radiation fins 24 and 30 provided on the back side of the fixed scroll 18 and the orbiting scroll 20, respectively, so that the air is fixed.
  • the scroll 18 and the orbiting scroll 20 are cooled.
  • the outside air introduced into the third air passage 60 is supercharged to the introduction passage 15 of the compressor body 4.
  • the air guide space 57 formed by the lid portion 53 and the cover 63 communicates with the filter casing 10 of the filter unit 2 disposed above (that is, below the filter casing 10, the air guide space 57 is provided.
  • the opening 120 is provided so as to communicate with the Therefore, the outside air supplied from the third air passage 60 is sent to the filter unit 2 via the air guide space 57.
  • the outside air sent from the air guide space 57 passes through the filter element 14 to remove foreign matter, and is then supercharged to the compressor body 4.
  • the cooling air supercharged to the compressor body 4 is supercharged through the air guide space 57.
  • the air guide space 57 By passing through the air guide space 57 in this way, the dynamic pressure of the cooling air from the duct 54 is converted into a static pressure and is supercharged to the compressor body 4. Therefore, even when there is a variation such as pulsation in the supply gas from the duct 54, stable supercharging can be realized.
  • the air guide space 57 is formed to have a larger flow path area than the duct 54, the dynamic pressure of the cooling air sent from the duct 54 can be satisfactorily converted to static pressure, and stable supercharging is possible. It has become.
  • the cover 63 constituting the air guide space 57 has a curved inner wall so as to rectify the cooling air introduced into the air guide space 57 toward the introduction path 15 of the compressor body 4. As a result, the cooling air introduced into the air guide space 57 via the third air passage 60 is efficiently guided to the introduction passage 15 of the compressor body 4, and good supercharging is possible.
  • the air guide space 57 is used to supercharge the outside air from the third air passage 60 to the compressor body 4.
  • the discharge pipe It may also be used to cool the pressurized gas passing through 59.
  • each of the above embodiments is a so-called belt-driven scroll fluid machine in which the drive shaft 22 rotates through a transmission belt that is rotated by a power source such as an electric motor or an engine.
  • a power source such as an electric motor or an engine.
  • the present invention is not limited to a belt-driven scroll fluid machine.
  • the present invention can also be applied to, for example, a so-called direct power source type scroll fluid machine in which a turning plate 32 is directly connected to one end of a drive shaft of a power source and a blower fan 52 is fixed to the other end of the drive shaft. It is.
  • the scroll compressor according to each of the above embodiments is a compressor having the fixed scroll 18 and the orbiting scroll 20.
  • the present invention is not limited to such a scroll compressor.
  • the present invention can also be applied to a scroll fluid machine constituted by a driving scroll as a first scroll and a driven scroll as a second scroll.
  • At least one embodiment of the present invention is applicable to a scroll fluid machine.

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  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne une machine à fluide à volutes, qui comporte : un corps de compresseur ayant une première volute et une seconde volute qui forment une chambre de compression ; un capot qui forme un espace de guidage d'air en recouvrant au moins une partie du corps de compresseur ; et un ventilateur de soufflante qui délivre de l'air de refroidissement pour refroidir au moins l'une parmi la première volute et la seconde volute. Une partie de l'air de refroidissement est suralimentée au niveau d'un orifice d'admission de la chambre de compression à travers l'espace de guidage d'air, et une bonne efficacité de compression est obtenue avec une configuration simple.
PCT/JP2018/013817 2017-03-31 2018-03-30 Machine à fluide à volutes Ceased WO2018181977A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP18778176.0A EP3604811B1 (fr) 2017-03-31 2018-03-30 Machine à fluide à volutes
CN201880022378.8A CN110475972B (zh) 2017-03-31 2018-03-30 涡旋流体机械
US16/583,877 US20200018313A1 (en) 2017-03-31 2019-09-26 Scroll fluid machine

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP2017072642A JP2018173053A (ja) 2017-03-31 2017-03-31 スクロール流体機械
JP2017-072639 2017-03-31
JP2017072639A JP2018173050A (ja) 2017-03-31 2017-03-31 スクロール流体機械
JP2017072640A JP2018173051A (ja) 2017-03-31 2017-03-31 スクロール流体機械
JP2017-072640 2017-03-31
JP2017-072641 2017-03-31
JP2017-072642 2017-03-31
JP2017-072638 2017-03-31
JP2017072641A JP2018173052A (ja) 2017-03-31 2017-03-31 スクロール流体機械
JP2017072638A JP6928471B2 (ja) 2017-03-31 2017-03-31 スクロール流体機械

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US16/583,877 Continuation US20200018313A1 (en) 2017-03-31 2019-09-26 Scroll fluid machine

Publications (1)

Publication Number Publication Date
WO2018181977A1 true WO2018181977A1 (fr) 2018-10-04

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PCT/JP2018/013817 Ceased WO2018181977A1 (fr) 2017-03-31 2018-03-30 Machine à fluide à volutes

Country Status (4)

Country Link
US (1) US20200018313A1 (fr)
EP (1) EP3604811B1 (fr)
CN (1) CN110475972B (fr)
WO (1) WO2018181977A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115126684B (zh) * 2022-06-24 2023-08-08 清华大学 双模态压缩机
CN119062573A (zh) * 2023-06-01 2024-12-03 罗伯特·博世有限公司 压缩机及其动涡盘

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JPS58146894U (ja) * 1982-03-29 1983-10-03 トキコ株式会社 スクロ−ル圧縮機
JP2001336488A (ja) * 1999-09-27 2001-12-07 Tokico Ltd スクロール式流体機械
JP2010196677A (ja) 2009-02-27 2010-09-09 Anest Iwata Corp 空冷式スクロール圧縮機

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JPS58146849U (ja) * 1982-03-29 1983-10-03 株式会社小松製作所 シリンダブロツク
EP0863313A1 (fr) * 1997-03-04 1998-09-09 Anest Iwata Corporation Compresseur à volutes à deux étages
JP2002266777A (ja) * 2001-03-07 2002-09-18 Anest Iwata Corp 多段式流体圧縮部を備えたスクロール流体機械
JP4591350B2 (ja) * 2003-07-28 2010-12-01 ダイキン工業株式会社 冷凍装置
CN101900113B (zh) * 2009-05-15 2013-10-30 艾默生环境优化技术有限公司 压缩机和油冷却系统
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WO2014156743A1 (fr) * 2013-03-28 2014-10-02 三菱電機株式会社 Compresseur à spirale et dispositif de cycle de réfrigération le comprenant
CN105971875B (zh) * 2016-06-20 2018-09-11 浙江蓝德华燕动力有限公司 一种无油润滑两级式涡旋压缩机

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JPS58146894U (ja) * 1982-03-29 1983-10-03 トキコ株式会社 スクロ−ル圧縮機
JP2001336488A (ja) * 1999-09-27 2001-12-07 Tokico Ltd スクロール式流体機械
JP2010196677A (ja) 2009-02-27 2010-09-09 Anest Iwata Corp 空冷式スクロール圧縮機

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Title
See also references of EP3604811A4

Also Published As

Publication number Publication date
EP3604811A1 (fr) 2020-02-05
CN110475972B (zh) 2021-03-02
EP3604811A4 (fr) 2020-11-18
EP3604811B1 (fr) 2022-08-17
US20200018313A1 (en) 2020-01-16
CN110475972A (zh) 2019-11-19

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