CN116971993A

CN116971993A - Encapsulated rotary pump unit

Info

Publication number: CN116971993A
Application number: CN202310978619.9A
Authority: CN
Inventors: 福岛一树; 长谷部高正; 吉田洋介; 原山真吾
Original assignee: Orion Machinery Shanghai Co Ltd; Orion Machinery Co Ltd
Current assignee: Orion Machinery Shanghai Co Ltd; Orion Machinery Co Ltd
Priority date: 2021-07-16
Filing date: 2022-05-26
Publication date: 2023-10-31
Also published as: WO2023286466A1; CN115768984A

Abstract

The application provides a sealed rotary pump unit, which can prevent the overheat of the air in a sealed box even if a rotary pump in the sealed box is used as a vacuum pump in a high vacuum degree range, thereby maintaining high pump performance and prolonging the service life of the device. The package type rotary pump unit is provided with: an electric rotary pump (200) provided with a rotary pump (2) for sucking/discharging gas and an electric motor (3); and a sealed case (1) in which the electric rotary pump (200) is incorporated, and which is provided with: a liquid-cooled heat exchanger (5) which is disposed inside the sealed case (1) and which is cooled by receiving a supply of a cooling liquid from a cooling liquid supply source (4) disposed outside the sealed case (1); and an air supply device (6) which is disposed inside the sealed case (1) and which supplies, to the liquid-cooled heat exchanger (5), the internal air in the sealed case (1) containing the heated air generated by the heating of the air around the rotary pump (2) by the operation of the rotary pump (2), so as to cool the internal air.

Description

Encapsulated rotary pump unit

The application is a divisional application of the application name of a packaged rotary pump unit, wherein the application date is 2022, 05, 26 and 202280003975.2.

Technical Field

The present application relates to a package type rotary pump unit, comprising: an electric rotary pump provided with a rotary pump for sucking and discharging gas and an electric motor for driving the rotary pump; and a sealed case in which the electric rotary pump is incorporated.

Background

As a conventional sealed rotary pump unit, the present inventors have proposed an exhaust temperature adjustment system for an air pressure apparatus station, which is provided with at least one of an air pressure apparatus, a storage box capable of storing a plurality of air pressure apparatuses and capable of insulating sound by storing the air pressure apparatus in a closed space, an air supply apparatus for cooling the storage box heated by the air pressure apparatus to generate a cooling air flow flowing substantially upward from below in the storage box for taking in external air and discharging the cooling air flow, a water temperature control unit for controlling the water temperature to adjust the temperature of the cooling water supplied to the cooling air, and a flow control unit for controlling the flow rate to adjust the flow rate of the cooling water supplied to the cooling air, wherein the air supply apparatus is provided with an air flow rate support portion in a height direction of the storage box, and the air pressure adjustment device has a cooling air flow support portion (see the air flow support portion 1) in a height direction in the storage box, and is provided with at least one of cooling air flow support portions.

As an example of a rotary pump incorporated in a package-type rotary pump unit, as shown in fig. 22, the present inventors have proposed a rotary pump (claw pump) including a cylinder portion 10a, one end wall portion 10b provided on one end surface of the cylinder portion 10a, and the other end wall portion 10c provided on the other end surface of the cylinder portion 10a so as to form a pump chamber 10 having a cross-sectional shape in which portions of two circles overlap, the rotary pump including: two rotary shafts 20A, 20B disposed in parallel in the pump chamber 10 and rotated at the same speed in opposite directions; two rotors 30A and 30B provided in the two rotary shafts 20A and 20B, respectively, and disposed in the pump chamber 10, and having hook-shaped claw portions formed so as to be rotatable without contact with each other, thereby compressing and discharging the sucked gas; and a discharge-side opening 50 provided so as to be opened at a position of at least one of the end wall 10B and the end wall 10c and facing the position of the compressed gas in the pump chamber 10, wherein the discharge-side opening 50 is provided with a front-stage vent 51 and a rear-stage vent (vent 55), the front-stage vent 51 is provided so as to be communicated with the outside of the pump chamber 10 at a front stage where the compression ratio of the gas is maximized by the claw portions of the two rotors 30A, 30B, the rear-stage vent (vent 55) is provided so as to be communicated with the outside of the pump chamber 10 at a stage where the compression ratio of the gas is maximized by the claw portions of the two rotors 30A, 30B, the front-stage vent 51 is closed by the rotor 30A at a stage where the compression ratio of the gas is maximized by the claw portions of the two rotors, the pump body is provided so as to be communicated with the outside of the pump chamber 10, the two bearing portions are provided so as to be separated by the bearing portions 20A, and the two bearing portions 20B are provided so as to be separated by the bearing portions 20A, and the bearing portions 20B are provided at the end wall portions 20B, respectively.

According to the claw pump proposed by the present inventors, the exhaust side opening portion 50 is constituted by a front stage air vent 51 and a rear stage air vent (air vent 55) which are provided so as to be opened respectively. Therefore, for example, when the pump is used as a vacuum pump at a high vacuum level, the intake of unheated outside air into the pump chamber 10 through the front-stage air port 51 can suppress the reverse flow of exhaust air through the rear-stage air outlet (air outlet 55), thereby preventing overheating of the pump chamber 10 and improving the pump performance.

Prior art literature

Patent literature

Patent document 1: (Japanese patent publication No. 5041849) (claim 1, FIG. 1)

Patent document 2: (Japanese patent publication No. 6749714) (claims 1, FIG. 3)

Disclosure of Invention

Problems to be solved by the application

In the conventional sealed rotary pump unit, although it is proposed to introduce cooling air from the outside and discharge air heated by the rotary pump to the outside of the casing, there is no proposal for effectively preventing overheating in the sealed casing when the rotary pump is placed in the sealed casing and the air heated by the rotary pump cannot be discharged to the outside of the sealed casing. That is, if the temperature of the internal air increases due to overheating of the sealed casing caused by the operation of the rotary pump, the electric motor, the electric components, and the like will be adversely affected, and therefore, an appropriate temperature countermeasure is required.

Accordingly, an object of the present invention is to provide a sealed rotary pump unit capable of preventing the overheat of the air inside the sealed casing, maintaining high pump performance and prolonging the service life of the device even when the heat generation amount of the rotary pump incorporated in the sealed casing is large when the rotary pump is used in a high vacuum range as a vacuum pump, for example.

Means for solving the problems

The present invention has the following configuration to achieve the above object.

According to one aspect of the present invention, there is provided a packaged rotary pump unit comprising: an electric rotary pump provided with a rotary pump for sucking/discharging gas and an electric motor for driving the rotary pump; and a sealed case in which the electric rotary pump is incorporated, wherein the sealed rotary pump unit includes: a liquid-cooled heat exchanger disposed inside the sealed case and cooled by receiving a supply of a cooling liquid from a cooling liquid supply source disposed outside the sealed case; and an air blowing device that is disposed inside the sealed case and that feeds, to the liquid-cooled heat exchanger, internal air in the sealed case including heated air, the internal air being cooled, wherein the heated air is generated by heating air around the rotary pump by operation of the rotary pump, the rotary pump is a biaxial rotary pump, one rotor rotation shaft is connected in series to a rotation shaft of the electric motor and rotates, the other rotor rotation shaft rotates in synchronization with the one rotor rotation shaft through a gear, and the liquid-cooled heat exchanger and the air blowing device are disposed in a space adjacent to a portion on an extension line where an axial center of the other rotor rotation shaft is disposed, that is, a portion connected to the electric motor and the one rotor rotation shaft.

In addition, according to an aspect of the present invention, there is provided a rotary pump unit including a pump cover portion which is disposed in the sealed case so as to cover the rotary pump, and which is configured to include: a circulating air inlet portion for introducing the internal air circulating inside the sealed case; and a circulating air outlet portion that discharges the internal air including the heated air. The pump cover may be provided to cover the periphery of the rotary pump except for the electric motor in the electric rotary pump, and the circulating air inlet may be provided to surround the periphery of the rotary pump and be opened in a band shape. More specifically, the rotary pump may include a bearing body portion, a pump chamber body portion, and a first muffler portion, and the pump cover portion may be provided so as to cover the periphery of the bearing body portion and the pump chamber body portion.

In addition, according to an aspect of the present invention, the liquid-cooled heat exchanger is connected to the circulating air outlet portion side, and the air blowing device is connected to the liquid-cooled heat exchanger so as to suck the internal air, and the internal air may flow from the circulating air inlet portion to the circulating air outlet portion and pass through the liquid-cooled heat exchanger.

In addition, according to an aspect of the present invention, the rotary pump may be connected to the coolant supply source to be cooled.

In addition, according to an aspect of the present invention, there is provided a packaged rotary pump unit comprising: an electric rotary pump provided with a rotary pump for sucking/discharging gas and an electric motor for driving the rotary pump; and a sealed case in which the electric rotary pump is incorporated, wherein the sealed rotary pump unit includes: a liquid-cooled heat exchanger disposed inside the sealed case and cooled by receiving a supply of a cooling liquid from a cooling liquid supply source disposed outside the sealed case; and an air blowing device that is disposed inside the sealed case and that feeds, to the liquid-cooled heat exchanger, internal air in the sealed case including heated air generated by heating air around the rotary pump by operation of the rotary pump, wherein a liquid-cooled flow path from the cooling liquid supply source is connected in series across the liquid-cooled heat exchanger and the rotary pump so that the rotary pump is also cooled by the cooling liquid from the cooling liquid supply source that cools the liquid-cooled heat exchanger.

In addition, according to an aspect of the present invention, the rotary pump includes a bearing main body portion, a pump chamber main body portion, and a first muffler portion, and the liquid cooling flow paths from the cooling liquid supply source are connected in series so that the cooling liquid from the cooling liquid supply source flows through the liquid cooling heat exchanger, the bearing main body portion, the pump chamber main body portion, and the first muffler portion in this order.

In addition, according to an aspect of the present invention, the electric motor may be provided with an air-sending fan for cooling the electric motor to send air to cool the electric motor, and the air-sending fan may be provided so as to be disposed on a side opposite to a side connected to the one rotor rotation shaft to send air to the motor main body.

Effects of the invention

According to the packaged rotary pump unit of the present invention, the following particularly advantageous effects can be achieved: even when the rotary pump is operated in a high-temperature environment and the heat generation amount is large when the rotary pump is used as a vacuum pump in a high-vacuum range, for example, the internal air of the sealed box can be prevented from overheating, so that high pump performance can be maintained and the service life of the device can be prolonged.

Drawings

Fig. 1 is a block diagram schematically showing the liquid cooling flow and the circulating gas (air) flow in the sealed case of the package type rotary pump unit according to the present invention.

Fig. 2 is a block diagram schematically showing the cold flow and the exhaust flow of the case of the packaged rotary pump unit of the present invention.

Fig. 3 is a perspective view showing the inside of a sealed casing of an embodiment example of the sealed rotary pump unit of the present invention.

Fig. 4 is a perspective view showing a state in which the pump cover portion of the embodiment of fig. 3 is removed.

Fig. 5 is a plan view of the electric rotary pump according to the embodiment of fig. 3.

Fig. 6 is a plan view showing a state in which the pump cover portion of the embodiment of fig. 5 is removed.

Fig. 7 is a rear view of the case of fig. 3.

Fig. 8 is a perspective view showing the appearance of a case where two electric rotary pumps of the package type rotary pump unit of the present invention are housed in two stages.

Fig. 9 is a perspective view showing an internal structure of the sealed case of the embodiment example of fig. 8.

Fig. 10 is a side view showing an internal structure of the sealed box of the embodiment example of fig. 8.

Fig. 11 is a perspective view showing a state in which a switchboard is removed from the internal structure of the sealed case of the embodiment example of fig. 8.

Fig. 12 is a front view showing a state in which a switchboard is removed from the internal structure of the sealed case of the embodiment example of fig. 8.

Fig. 13 is a perspective view showing a configuration example of a rotary pump (claw pump) mounted on a package type rotary pump unit according to the present invention, in which the rotary pump is sectioned in a stepped manner.

Fig. 14 is a front perspective view of the embodiment of fig. 13.

Fig. 15 is a rear perspective view of the embodiment of fig. 13.

Fig. 16 is a front view of the case of fig. 13.

Fig. 17 is a rear view of the case of fig. 13.

Fig. 18 is a top view of the case of fig. 13.

Fig. 19 is a perspective view showing a cross section of the bearing portion coolant flow passage in the example of fig. 13.

Fig. 20 is an exploded view showing a coolant flow field forming surface as an inner surface of the first flow field forming portion in the example of fig. 13.

Fig. 21 is an exploded view of an exhaust flow path forming surface that is an outer surface of the first flow path forming portion in the example of fig. 1.

Fig. 22 is an exploded view showing a conventional rotary pump.

Detailed Description

An example of an embodiment of the package type rotary pump unit according to the present invention, in which a claw pump is mounted as an example of a rotary pump, will be described in detail below with reference to the drawings (fig. 1 to 21). Further, an example of the rotary pump of the present invention is a vacuum pump, and is a water-cooled biaxial rotary pump (claw pump). However, the rotary pump of the present invention is not limited to this embodiment, and includes: the present invention can be used as a pump such as a blower that uses the discharged gas as a product gas, a pump including a single-shaft rotary pump such as a vane pump, or a pump that uses water as a cooling liquid.

The package-type rotary pump unit according to the present invention includes, as a basic structure: an electric rotary pump 200 including a rotary pump 2 for sucking and discharging gas and an electric motor 3 for driving the rotary pump 2; and a sealed case 1 in which the electric rotary pump 200 is incorporated.

The airtight enclosure 1 of the present invention does not need to be tightly sealed, and may be any enclosure that forms a closed space that sufficiently restricts the outflow/inflow of gas (in this case, air) between the inside of the enclosure and the outside, and that has a degree of tightness that is not substantially affected by outside air (outside air) or the circulation of the inside air in the airtight enclosure 1. That is, in the sealed case 1 of the present invention, a small gap is allowed, and instead of using a sealing material as in the present case, a structural member such as a steel plate constituting the case may be brought into contact with each other to sufficiently restrict the air flow tightness.

The sealed case 1 of this embodiment has a rectangular box shape, and includes a case frame portion 1a (see fig. 3, 9, etc.), a base portion 1b (see fig. 3, 9, etc.), and a case cover portion 1c (see fig. 8). The sealed case 1 is configured such that a case frame portion 1a having a lattice structure formed of square steel pipes, angle steel, or the like is covered with a case cover portion 1c formed of a steel plate or the like.

The sealed case 1 is internally provided with: an electric rotary pump 200 including a rotary pump 2 and an electric motor 3, a liquid-cooled heat exchanger 5, an air blower 6, a pump cover portion 25, a distribution board 8, a first muffler portion 31, a second muffler portion 32, an air blower 9 for cooling electric components, a dew receiving tray 91, various pipes, various electric wires, and accessories thereof.

As shown in fig. 1 and 3 to 7, reference numeral 5 denotes a liquid-cooled heat exchanger which is disposed inside the sealed case 1 and is configured to be cooled by receiving a supply of a coolant from a coolant supply source 4 disposed outside the sealed case 1. That is, the coolant supply source 4 is connected to the liquid-cooled heat exchanger 5 via the coolant supply connection port 4a and the coolant supply pipe 4 b. In fig. 1, the flow of the coolant is schematically shown by double-line arrows.

The liquid-cooled heat exchanger 5 of this embodiment is in the form of a so-called fin and tube, that is, a heat exchange tube 5a through which a cooling liquid flows is housed in a rectangular box-shaped heat exchange chamber in a state of being wound back and forth (zigzag shape). In the rectangular box-shaped heat exchange chamber of the present embodiment, a rectangular inlet port as a side for introducing the internal air (circulating air) is connected to a circulating air outlet port 25b of a pump cover 25 described later, and a rectangular outlet port as a side for discharging the internal air (circulating air) is connected to a blower 6 described later. Thereby, a fan cooler having the liquid-cooled heat exchanger 5 is constituted. The liquid-cooled heat exchanger 5 is of a general form, and therefore, detailed illustration thereof is omitted. As the liquid-cooled heat exchanger 5, the form of the flow path of the cooling liquid and the form of the flow path of the circulating air cooled by heat exchange can be appropriately and selectively set.

Here, the coolant supply source 4 may use a liquid cooling device that cools a liquid by a refrigeration cycle. It is needless to say that other cooling sources such as air (outside air), fresh water, sea water, ice, and ground water may be used depending on the site conditions or the like, and a plurality of cooling sources may be used in combination as appropriate. The coolant in this embodiment is cooling water, and is supplied from the coolant supply source 4 in the same manner as the coolant for cooling the exhaust gas discharged from the exhaust port 55 as described later.

Further, 6 is an air blowing device, which is disposed inside the sealed case 1, and is configured as the following means: the internal air in the sealed case 1 containing the heated air generated by the operation of the rotary pump 2 by heating the air around the rotary pump 2 is sent to the liquid-cooled heat exchanger 5 to cool the air. Further, in fig. 1, the flow of the inside air is schematically shown with bold arrows.

The blower 6 in this embodiment is an axial flow fan, and is configured to suck and discharge the internal air along the longitudinal direction of the electric rotary pump 200. The blower 6 is not limited to an axial flow fan, and other blower units such as a centrifugal fan (e.g., a sirocco fan) may be optionally used.

According to the sealed rotary pump unit of the present invention, even when the rotary pump 2 incorporated in the sealed casing 1 is operated in a high-temperature environment, for example, when the rotary pump is used as a vacuum pump in a high-vacuum range and generates a large amount of heat, the internal air of the sealed casing 1 can be prevented from overheating, and thus the following advantageous effects can be achieved: high pump performance can be maintained and the life of the device can be prolonged. That is, the air blowing device 6 causes the internal air in the sealed case 1 to flow, and the superheated air is prevented from stagnating around the rotary pump 2 by the liquid-cooled heat exchanger 5, so that the internal air can be efficiently circulated and cooled. Therefore, the temperature rise in the sealed case 1 caused by heat generation of the rotary pump 2 or the like can be appropriately suppressed, and adverse effects on the electric motor 3, electric components, and the like can be prevented, so that high pump performance can be maintained, and the device lifetime can be prolonged.

In addition, since the entire or most of the heat discharged to the outside of the sealed case 1 is mediated by the cooling liquid (cooling water) for heat exchange, the heat dissipation to the surroundings can be minimized, and there is an advantage in that the influence on the installation environment is extremely small. For example, the air conditioning load of a room in which the package-type rotary pump unit of the present invention is provided can be reduced.

Further, the closed structure is formed by the closed casing 1, and therefore, there is an advantage in that the operation sound reduction effect is large. Furthermore, according to the embodiment of the airtight structure of the airtight enclosure 1 of the present embodiment, the noise can be reduced to 73dB.

Further, by forming the closed structure by the closed casing 1 in this way, the inflow and outflow of the gas between the inside of the casing and the outside can be sufficiently restricted, and therefore, even in a high humidity environment, the amount of condensate generated in the inside of the casing is small. That is, if the cooling liquid can be supplied, the internal temperature of the sealed case 1 is less likely to be affected by the product installation environment (temperature and humidity), and therefore, the sealed case can be used in a wide range of environmental temperature and humidity ranges.

As will be described later, in this case, the first muffler section 31 and the second muffler section 32 are housed in the sealed case 1, and the inside air of the sealed case 1 including heat emitted from these muffler sections can be cooled.

In this case, the pump housing 25 is provided, and the pump housing 25 is disposed inside the hermetic container 1 so as to cover the rotary pump 2, and is formed so as to be provided with: a circulating air inlet 25a for introducing the internal air circulating inside the sealed case 1; and a circulating air outlet portion 25b that discharges the internal air including the heated air. The position of the blower 6 relative to the pump cover 25 is not limited to this case, and may be set selectively as appropriate as long as the internal air can flow so as to be introduced from the circulating air inlet 25a and discharged from the circulating air outlet 25b.

According to the pump cover portion 25, heat generated by the rotary pump 2 can be retained inside the pump cover portion 25, and the heat can be prevented from being emitted outside the pump cover portion 25 and dispersed throughout the space in the sealed case 1. By doing so, the heat generated by the rotary pump 2 is not dispersed, and high-temperature air (heated air) can be sent to the liquid-cooled heat exchanger 5 in a concentrated state, so that the heated air can be cooled effectively. That is, the temperature difference between the heated air and the liquid-cooled heat exchanger 5 can be further increased, heat exchange can be efficiently performed, and the temperature rise in the sealed case 1 can be effectively suppressed. Further, since the high-temperature air is sent to the liquid-cooled heat exchanger 5 in a concentrated state, the circulating air outlet portion 25b is formed in a reduced flow path, and thus the liquid-cooled heat exchanger 5 can be miniaturized, and the product cost can be reduced.

The pump cover portion 25 of the present embodiment is provided such that a circulating air inlet portion 25a which surrounds the periphery of the rotary pump 2 and is opened in a band shape is formed on the exhaust side (the side opposite to the side to which the electric motor 3 is connected) of the rotary pump 2 so that the outer surface thereof can be cooled effectively by causing the inside air to flow in such a manner as to be in effective contact with the entire outer surface of the rotary pump 2. The circulating air outlet portion 25b for discharging the internal air including the heated air heated by the rotary pump 2 is formed in a flow path reduced diameter so as to intensively guide the internal air to the liquid-cooled heat exchanger 5. Further, in this case, the circulating air outlet 25b is connected in an airtight sealed state to the inlet of the internal air of the heat exchange chamber of the liquid-cooled heat exchanger 5. This can appropriately generate the flow of the internal air, appropriately circulate the internal air, efficiently exchange heat, and efficiently suppress the temperature rise in the sealed case 1.

In this case, the inlet of the liquid-cooled heat exchanger 5 is connected to the circulating air outlet 25b side, and the blower 6 is connected to the liquid-cooled heat exchanger 5 so as to suck the internal air and flow the internal air from the circulating air inlet 25a to the circulating air outlet 25b, and the internal air passes through the liquid-cooled heat exchanger 5. In this case, the inlet of the air blowing device 6 is connected to the outlet of the heat exchange chamber of the liquid-cooled heat exchanger 5 in an airtight state.

This can reasonably and effectively generate a smooth flow of the internal air, effectively circulate the internal air, and efficiently perform heat exchange, thereby effectively suppressing a temperature rise in the sealed case 1. In addition, by disposing the blower 6 in the liquid-cooled heat exchanger 5 as in this case, the blower 6 itself sucks the air cooled by the liquid-cooled heat exchanger 5, thereby preventing overheating and prolonging the lifetime of the apparatus.

In this case, the pump cover portion 25 (see fig. 3 to 6, etc.) is provided so as to cover the ranges of the pump chamber main body portion 110 and the bearing main body portion 120 (see fig. 13 to 18, etc.) of the rotary pump 2. That is, as will be described later, the portion other than the portion where the surface temperature of the liquid-cooled first muffler portion 31 is high is effectively covered. In addition, the size of the gap (the width of the ventilation passage) provided between the inner surface of the pump cover portion 25 and the outer surface of the rotary pump 2 so as to form the circulating air inlet portion 25a adaptively may be set within the following range: the ventilation resistance when the internal air flows is kept as small as possible, and the internal air heated by the heat generated by the rotary pump 2 (heated air) is kept as small as possible from being dispersed outside the pump cover 25.

In this case, the rotary pump 2 is a biaxial rotary pump, in which one rotor rotation shaft (rotation shaft 20A) is connected in series to the rotation shaft 3a of the electric motor 3 and rotates, the other rotor rotation shaft (rotation shaft 20B) rotates synchronously with a gear in a direction opposite to the one rotor rotation shaft (rotation shaft 20A), and the liquid-cooled heat exchanger 5 and the blower 6 are disposed in the following space: is located on an extension line of the shaft center of the rotary shaft 20B where the other rotor rotary shaft (rotary shaft 20B) is disposed, and is adjacent to a portion where the electric motor 3 and the one rotor rotary shaft (rotary shaft 20A) are connected.

This makes it possible to properly circulate the inside air by properly utilizing the inside space of the sealed case 1.

As shown in fig. 4 and the like, one rotor rotation shaft (rotation shaft 20A) and the rotation shaft 3a of the electric motor 3 in this embodiment are connected in series via a coupling 3 b. As shown in fig. 3 and the like, 3c is a safety cover, and covers a connection portion including the rotation shafts (3 a, 20A) of the rotation-driven coupling 3b for safety. Further, an air blowing blade may be mounted coaxially with the rotation shafts (3 a, 20A) to the coupling 3b to blow air. According to this blower blade, the cooling performance can be improved.

In this case, an air-blowing fan 7 for cooling the electric motor is provided to the electric motor 3 so as to cool the electric motor 3, and the air-blowing fan 7 is provided so as to blow air toward the motor main body with a rotation shaft disposed on the opposite side to the side connected to one rotor rotation shaft (rotation shaft 20A).

As a result, as indicated by the thick arrow in fig. 1, a smooth circulation flow of the internal air can be generated reasonably and effectively, heat exchange can be performed efficiently, and a temperature rise in the sealed case 1 can be suppressed efficiently. That is, as shown in fig. 1, first, the inside air is heated by being sucked by the blower 6, passes through the inside of the pump cover 25, and then is cooled by the liquid-cooled heat exchanger 5. Next, the internal air sucked from the liquid-cooled heat exchanger 5 is discharged in a direction separating from the rotary pump 2 (leftward in fig. 5 from the blower 6) by the blower 6, and flows laterally of the electric motor 3 (upward in fig. 5 from the electric motor 3). Then, the internal air cooled by the liquid-cooled heat exchanger 5 and discharged from the blower 6 hits the inner surface of the closed casing 1, and a part of the internal air is sucked by the blower fan 7 of the electric motor 3 and is reversed, flows so as to cool the motor main body of the electric motor 3, and then flows to the main body side of the rotary pump 2. The internal air flowing around the pump cover 25 is reversed, and is sucked from the circulating air inlet 25a to the inside of the pump cover 25 by the suction force of the blower 6. As described above, by generating the air flow, the internal air can be circulated appropriately, heat exchange can be performed efficiently, and the temperature rise in the sealed case 1 can be suppressed efficiently.

Further, in this case, as shown in fig. 1, 9 and 10, an air cooling unit for flowing air in a small-chamber-shaped switchboard 8 is provided to a switchboard 8 formed on the front surface side of a closed casing 1, and an air blower 9 for cooling electric components is mounted on the lower portion of the switchboard 8.

According to the blower 9 for cooling electric components of the present embodiment, it is possible to blow air so as to suck a part of the internal air (cooling air) in the sealed case 1 into the switchboard 8, flow the air upward from below in the switchboard 8, and discharge the air from an opening in an upper portion, not shown, in the switchboard 8. This can effectively cool the highly exothermic electric components 82, the inverter 83, and the like provided in the switchboard 8. In addition, the internal air discharged from the distribution board 8 is sucked into the pump cover 25 from the circulating air inlet 25a of the pump cover 25. As shown in fig. 9 and 10, since 81 is an operation unit and has low heat generation, in this case, the air cooling unit is not provided alone but is disposed at a position separated from the switchboard 8.

In this case, as described in detail with reference to fig. 13 to 21, the rotary pump 2 is connected to the coolant supply source 4 to be liquid-cooled. In this case, the pipes of the coolant flowing from the coolant supply source 4 are connected in series so that the coolant first passes through the liquid-cooled heat exchanger 5, and then the exhaust gas discharged from the exhaust port 55 (see fig. 13, etc.) is cooled. In this way, both the liquid-cooled heat exchanger 5 and the rotary pump 2 are liquid-cooled, and thus the temperature rise in the sealed case 1 can be effectively suppressed.

Next, a specific example of the flow path of the coolant supplied from the coolant supply source 4 will be described with reference to the drawings (fig. 1, 3, 7, 9 to 15, etc.).

The coolant supply source 4 is connected to a coolant supply connection port 4a provided on the back surface of the closed casing 1, and the coolant is first supplied to the liquid-cooled heat exchanger 5 through a coolant supply pipe 4b from the coolant supply connection port 4a by a fluid pump (not shown), and cools the liquid-cooled heat exchanger 5. In the case where the electric rotary pump 200 is arranged in two stages as shown in fig. 9 to 12, the two coolant supply pipes 4b are branched, the two electric rotary pumps 200 in two stages are respectively supplied with the coolant, and the two coolant discharge pipes 4c are joined to discharge the coolant.

Next, the coolant whose internal air is cooled by the liquid-cooled heat exchanger 5 passes through the coolant connection pipe 5b (see fig. 1, 7, etc.), and is supplied to the coolant inlet connection 71a (see fig. 7, 15, etc.) to cool the rotary pump 2. Then, as will be described later with reference to fig. 13 to 21, the cooling liquid passes through the bearing portion cooling liquid passage 71, whereby the bearing portion 40 and the gear case 45 of the rotary pump 2 are cooled, and accordingly, the lubricating oil in the gear case 45 is cooled.

Next, as will be described later with reference to fig. 13 to 21, the coolant having passed through the bearing portion coolant flow passage 71 is introduced into the exhaust portion coolant flow passage 72, flows to cool the exhaust gas of the rotary pump 2, passes through the extension portion coolant flow passage 73, cools the exhaust portion of the rotary pump 2 and the portion constituting the first muffler portion 31, and is discharged from the extension portion coolant outlet connection portion 73 b. A coolant discharge pipe 4c is connected to the extension coolant outlet connection portion 73b, and an outlet end of the coolant discharge pipe 4c is a coolant discharge connection port 4d connected to the coolant supply source 4.

The cooling liquid circulates through the above flow paths, so that the liquid-cooled heat exchanger 5 and the rotary pump 2 can be cooled, and the cooling liquid that cools the internal air of the sealed case 1, the lubricating oil of the rotary pump 2, and the exhaust gas returns to the cooling liquid supply source 4 to circulate in this case. In addition, when groundwater or the like is used, it is needless to say that the water may not circulate but flow in one direction.

As a result, the liquid-cooled heat exchanger 5, the bearing portion 40 and the gear case 45 of the rotary pump 2, and the first muffler portion 31 serving as the exhaust portion of the rotary pump 2 can be successively and reasonably cooled by the coolant flowing through the liquid-cooled flow path connected in series across the liquid-cooled heat exchanger 5 and the rotary pump 2. That is, the temperatures of the respective portions are in such a temperature relationship that the allowable temperature of the oil stored in the gear case is higher than the allowable temperature of the internal air of the hermetic container 1, and the allowable temperature of the exhaust gas of the rotary pump is higher than the allowable temperature of the oil stored in the gear case, so that it is reasonable to flow the coolant in the above order. That is, when the three portions are cooled in this order, the coolant is gradually heated, but a temperature difference (a temperature difference between the coolant temperature and the temperature of the portion to be cooled) that can be sufficiently cooled can be maintained in each portion. The liquid-cooled piping connected in series simplifies the piping structure, and has the advantage of reducing the cost.

The liquid cooling piping is not limited to this case, and may be provided in parallel. According to the parallel arrangement, the flow rate thereof can be independently adjusted, and there is an advantage in that accurate cooling control can be realized.

Next, specific measurement data (verification values) will be described with respect to the cooling effect in the sealed case 1 in the example shown in fig. 1 to 7.

As an example of the condition of the highest assumed temperature, the temperature of the coolant (cooling water) was set to 32 ℃, and the temperature of each portion was measured to obtain data.

As comparative data, when the liquid-cooled heat exchanger 5 was not provided and the rotary pump 2 was provided to perform water cooling as in the example of the embodiment shown in fig. 13 to 21, the internal air of the sealed case 1 was raised to 80 ℃.

In contrast, in the case where the rotary pump 2 is water-cooled as described above and the liquid-cooled heat exchanger 5 is provided to water-cool the internal air as in the present embodiment, the temperature of the internal air at the circulating air outlet portion 25b of the pump cover portion 25 is 55 ℃, and the temperature of the internal air discharged from the blower 6 through the liquid-cooled heat exchanger 5 and circulated through the electric motor 3 and the distribution board 8 is 45 ℃. This makes it possible to sufficiently lower the heat-resistant temperature of the electric motor 3, the electric component 82, and the like. The temperature of the cooling water returned to the cooling liquid supply source 4 is 40 to 45 ℃.

The intake pipe of the rotary pump 2 is configured to be connectable to an external intake pipe through which the intake introduction connection port 16 can be connected, and to be capable of taking in external air. The check valve 17 is connected between the intake introduction connection port 16 and the intake port 15 of the rotary pump 2, and is provided so as to be capable of restricting the flow of gas from the pump 2 to the intake introduction connection port 16.

Further, 90 is a condensed water discharge connection port, and is a discharge port capable of discharging condensed water to the outside. The dew receiving tray 91 disposed under the rotary pump 2 and the dew receiving tray 93 for the heat exchanger disposed in the liquid-cooled heat exchanger 5 are connected to the condensate discharge connection port 90 via the condensate pipe 92 and the condensate pipe 94 for the heat exchanger, and can receive and appropriately discharge the condensate generated.

Next, the noise reduction structure of the package-type rotary pump unit according to the present invention will be described in detail with reference to the drawings (fig. 1 to 21). As described above, the package-type rotary pump unit of the present invention includes, as a basic structure: an electric rotary pump 200 including a rotary pump 2 for sucking and discharging gas and an electric motor 3 for driving the rotary pump 2; and a sealed case 1 in which the electric rotary pump 200 is incorporated.

The rotary pump 2 mounted on the sealed rotary pump unit of the present invention is provided with a first muffler portion 31, and the first muffler portion 31 serves as an exhaust gas cooling portion for cooling exhaust gas by the coolant supplied from the coolant supply source 4 disposed outside the sealed casing 1, thereby producing a noise reduction effect. Further, a second muffler portion 32 for introducing and silencing the exhaust gas passing through the first muffler portion 31 is disposed above the electric rotary pump 200 in the sealed case 1.

According to the package type rotary pump unit of the present invention, in the case where the rotary pump 2 is built in the hermetic container 1, the following advantageous effects can be achieved in particular: noise generated by the operation of the rotary pump 2 can be reduced more reasonably and effectively. That is, the first muffler portion 31 for cooling the exhaust gas of the rotary pump 2 with the coolant is provided, and the second muffler portion 32 is disposed at the upper portion of the electric rotary pump 200, so that the electric rotary pump 200 and the entire muffler (the first muffler portion 31 and the second muffler portion 32) can be effectively covered with the sealed case (the sealed case 1) described above. Therefore, the noise can be shielded and absorbed by including the sound leaking from the muffler, the piping in the middle, and the like, and the noise reducing effect can be effectively improved. The second muffler portion 32 disposed above the electric rotary pump 200 also has an effect of shielding noise generated from the electric rotary pump 200. According to the embodiment of the package type rotary pump unit of the present embodiment, noise can be reduced to 73dB, and high quietness can be achieved. Further, by disposing the second muffler portion 32 at the upper portion of the electric rotary pump 200, the foot space can be suppressed. In order to improve the sound absorbing performance, the sound absorbing material may be attached to the inner surface of the member constituting the sealed case 1.

In this case, the second muffler portion 32 is constituted by a plurality of noise reduction chambers which are provided in series in the same direction as the connection direction of the rotary pump 2 and the electric motor 3 and in the longitudinal direction of the sealed case 1.

Thus, the plurality of noise reduction chambers can be appropriately arranged in a limited space, and a sufficient noise reduction effect can be obtained. That is, in the electric rotary pump 200 of the present embodiment, the rotary pump 2 and the electric motor 3 are connected in series, and therefore, the closed casing 1 is also formed to be long in the present embodiment. The second muffler portion 32 can be appropriately disposed inside the horizontally long sealed casing 1 in accordance with the form of the electric rotary pump 200, and the entire structure can be compactly provided.

Further, as the internal structure of the second muffler portion 32, a form that improves the noise reduction (silencing) effect of expansion, shielding, sound absorption, and the like can be appropriately and selectively designed. For example, by adopting a form in which the noise reduction chamber is provided as three chambers and the three chambers are arranged in series, a compact structure with high noise reduction performance can be realized.

More specifically, for example, in this case, the second muffler portion 32 has a cylindrical outer shape elongated in the axial direction, and includes a noise reduction chamber on one end side, a noise reduction chamber on the intermediate portion, and a noise reduction chamber on the other end side in the longitudinal direction, and in the noise reduction chamber on the one end side, exhaust gas introduced from an exhaust pipe extending from the exhaust port 57 of the first muffler portion is discharged so as to expand from a portion of the perforated pipe that is the tip end side of the exhaust pipe, thereby performing noise reduction. Then, the pipe is connected so as to convey the exhaust gas from the noise reduction chamber on the one end side to the noise reduction chamber on the other end side, and the exhaust gas is discharged to the noise reduction chamber on the other end side, whereby the expansion is performed to reduce the noise. Further, the exhaust gas introduced into the noise reduction chamber at the other end side is reversely discharged to the noise reduction chamber at the intermediate portion through the vent hole provided in the partition wall between the noise reduction chamber at the other end side and the noise reduction chamber at the intermediate portion, so that the expansion is performed to reduce the noise, and the exhaust gas can be discharged from the noise reduction chamber at the intermediate portion to the outside through the exhaust gas discharge port 35 of the second muffler portion.

In this case, the second muffler portion 32 is provided in the sealed case 1 in a suspended state. That is, as shown in fig. 3, 9, and the like, the second muffler portion 32 formed in a cylindrical shape in this embodiment is fixed to the hanging member 37, and is provided in a state of hanging from the upper portion of the sealed case 1 to the inside, and the hanging member 37 is fixed to the upper portion of the case frame portion 1a and extends downward.

By using the space above the electric rotary pump 200, it is possible to provide a suitable volume having a high sound deadening effect due to expansion, and to appropriately and easily arrange a lightweight muffler (second muffler portion 32) as compared with other structural devices. Further, it is needless to say that the sound absorbing material may be appropriately adhered to the inner surface of each of the noise reduction chambers of the second muffler portion 32, thereby obtaining the sound absorbing effect by the sound absorption.

In this case, as shown in fig. 3, 4, 7, and 9 to 12, the electric rotary pump 200 is provided in the sealed case 1 via the vibration damping member 300, and the first muffler portion 31 and the second muffler portion 32 are connected via the vibration damping pipe 33. That is, in this embodiment, the electric rotary pump 200 is provided on the base portion 1b in the sealed case 1 via the damper member 300 including the vibration-damping rubber, and the vibration-damping pipe 33 is connected between the exhaust port 57 of the first muffler portion and the exhaust gas inlet 34 of the second muffler portion, so that the exhaust gas flows from the first muffler portion 31 to the second muffler portion 32.

Accordingly, since the electric rotary pump 200 is provided by the vibration damping member 300 and is connected to the second muffler portion 32 through the vibration damping pipe 33, the transmission of the vibration of the electric rotary pump 200 to the side of the sealed case 1 can be reduced, and the vibration-proof and noise-damping effects can be suitably obtained. In addition, since the transmission of the vibration of the electric rotary pump 200 to the second muffler portion 32 can be reduced, the second muffler portion 32 can be provided in the sealed case 1 appropriately and more easily.

In this case, as shown in fig. 8 to 12, the second muffler portion 32 is disposed on the back surface side of the inside of the sealed case 1, and the switchboard 8 is disposed on the front surface side, as shown in a package type rotary pump unit in which the electric rotary pump 200 is mounted in a plurality of layers (two layers in this case). This makes the switchboard 8 a shielding part, and can further reduce noise transmitted to the front surface side. This can further improve the working environment.

Next, as an example of a rotary pump used in the package type rotary pump unit of the present invention, an example of a claw pump will be described with reference to fig. 13 to 21.

As shown in fig. 13 and the like, in the claw pump, 110 is a pump chamber main body portion, and includes a cylinder portion 10a, one end wall portion 10b provided on one end surface of the cylinder portion 10a, and the other end wall portion 10c provided on the other end surface of the cylinder portion 10a so as to form a pump chamber 10 (see fig. 22) having a cross-sectional shape in which portions of two circles overlap.

The two rotary shafts 20A and 20B are disposed in parallel in the pump chamber 10, and are provided to rotate at the same speed in opposite directions by a pair of gears 21A and 21B. In this case, gears 21A (driving side gear) and 21B (driven side gear) are integrally and fixedly provided to the two rotation shafts 20A and 20B, respectively. The pair of gears 21A and 21B are engaged with each other in a gear case 45 formed of a bearing body 120.

The two rotors 30A and 30B are provided in correspondence with the two rotary shafts 20A and 20B, are disposed in the pump chamber 10, and are provided with hook-shaped claw portions so as to be rotatable without contact with each other, and compress and discharge the sucked gas (see fig. 22). The end wall portion 10B of one of the pump chamber main body 110 is located on the gear case 45 side in which the pair of gears 21A and 21B are incorporated, and the exhaust port 55 for exhausting gas is provided in at least the other end wall portion 10c of the pump chamber main body 110. Thus, a package type rotary pump unit, which is one type of biaxial rotary pump, is constituted.

In this case, the two rotors 30A and 30B are disposed so as to correspond to one ends (one ends) of the two rotary shafts 20A and 20B, and are supported in a cantilevered state, the two rotary shafts 20A and 20B are pivotally supported by the bearing portion 40, one end wall portion 10B of the pump chamber main body 110 is located on the bearing portion 40 side, and the other end wall portion 10c of the pump chamber main body 110 is provided with the exhaust port 55 for exhausting gas. Further, 15 is an intake port, which is provided at a position facing a portion where the gas in the pump chamber 10 is not compressed. The intake port 15 of this embodiment is provided in a form of an upper cutout in an upper corner of the pump chamber main body 110, across an upper wall of the cylinder portion 10a and one end wall portion 10 b. The suction connection port 14 is provided with a lower end connected to the suction port 15 and an upper end connected to an air compressor (not shown) via a pipe.

In the sealed rotary pump unit according to the present invention, an exhaust part coolant flow passage 72 for passing coolant is provided on the other end wall part 10c side of the pump chamber main body 110 to cool the exhaust gas discharged from the exhaust port 55. In this case (an example of the case of using as a vacuum pump), the state in which the exhaust gas is discharged from the exhaust port 55 is a state in which the pump chamber 10 is opened in communication with the atmosphere (air) which is outside air, and the exhaust gas is discharged to the atmosphere (air). The liquid of the coolant may be a liquid other than water, such as a mixed liquid (aqueous solution) with water, an oil, or the like, such as an antifreeze, although it is also needless to say that the liquid is represented by cooling water.

According to the sealed rotary pump unit of the present invention, even when the sealed rotary pump unit is used as a vacuum pump in a range where the degree of vacuum is high, the degree of vacuum being a value close to absolute vacuum, overheat of the pump chamber 10 can be prevented more positively and effectively, and the pump performance can be improved significantly.

That is, by providing the exhaust portion coolant flow passage 72 on the other end wall portion 10c side of the pump chamber main body portion 110, the exhaust gas just discharged from the exhaust port 55 can be effectively cooled by the coolant. Thus, even in the case of a vacuum pump used in a range where the vacuum degree is not less than a certain level, the rise in the internal temperature of the pump chamber 10 can be suppressed even when the vacuum pump is heated by the reverse flow of the exhaust gas. Therefore, the gap between the inner wall surface of the pump chamber 10 and the two rotors 30A and 30B can be set small, and leakage of gas due to the gap can be reduced, so that the pump efficiency can be improved.

In addition, according to the sealed rotary pump unit of the present invention, the clearance can be set small as described above, whereby the degree of the ultimate vacuum can be further improved, and the overheat can be prevented even if there is a reverse flow of the exhaust gas, whereby the opening area of the exhaust port 55 can be set larger, and a vacuum pump with a larger processing air volume can be constituted.

Further, according to the sealed rotary pump unit of the present embodiment, the other end wall portion 10c side provided with the most heated exhaust port 55 is locally and actively cooled. That is, the pump chamber main body 110 that generates a large temperature gradient (temperature difference) is configured to cool the exhaust gas by preferentially cooling the other wall portion 10c side, which is centered on the exhaust port 55, of the wall portions of the pump chamber main body 110 so as to reduce the temperature difference. By thus cooling the exhaust gas to prevent overheating of the pump chamber 10, it was confirmed that the internal temperature difference was reduced by about 140 ℃ in the example, and that the pump performance was significantly improved by increasing the ultimate vacuum to 97 kPa. In addition, conventionally, as a limit for performing the extreme continuous operation, only an operation in which the degree of the extreme vacuum reaches about 90kPa has been performed so as to avoid the occurrence of contact (internal interference) between the wall inner surface of the pump chamber 10 and the two rotors 30A and 30B. In contrast, according to the present invention, the breaking operation with a higher degree of ultimate vacuum can be continuously performed.

In the sealed rotary pump unit, since the compression ratio of the gas is high and the gas is heated and discharged, the portion of the exhaust port 55 is most likely to be overheated, and the portion of the other end wall portion 10c where the exhaust port 55 is formed is higher in temperature than the other portion. Further, when compared with the other end wall portion 10c, the other portion of the pump chamber main body 110 is low in temperature. Therefore, if the entire pump chamber main body 110 is cooled similarly by including the cylinder portion 10A or the like, the temperature difference between the exhaust port 55 of the other end wall portion 10c and other portions is maintained, and the problem of interference of the rotors 30A and 30B as operation portions due to thermal expansion cannot be eliminated.

In this case, a coolant inlet 72b (see fig. 20) for introducing the coolant into the exhaust-portion coolant flow field 72 is provided near the exhaust port 55, and a coolant flow restriction portion 61b for restricting the flow of the coolant introduced is provided at a portion where the exhaust-portion coolant flow field 72 is formed so that the coolant surrounds the vicinity of the exhaust port 55. As shown in fig. 20, the coolant flow restriction portion 61b of the present embodiment is provided in the form of a rib at a plurality of points (two points in the present embodiment) of the coolant flow passage forming surface 61a of the first passage forming portion 61 described later.

By cooling the portion of the pump chamber main body 110 centered on the exhaust port 55 (the periphery of the exhaust port 55), which is the most heated portion, the exhaust gas just exiting the exhaust port can be cooled effectively, and the temperature of the periphery of the exhaust port 55 and the temperature of the exhaust gas can be reduced, so that the periphery of the exhaust port 55 can be suppressed from being excessively heated and deformed unevenly due to thermal expansion. In this way, thermal expansion of the pump chamber main body 110 and the two rotors 30A and 30B can be suppressed uniformly, and therefore, the gap between them can be reduced, and the pump efficiency can be improved.

In the sealed rotary pump unit, the exhaust port 55 is usually provided at a portion corresponding to the lower portion of the pump chamber 10 (in this case, the lower portion of the other end wall portion 10 c) in view of driving stability. In this case, the coolant inlet 72b is disposed as described above, and the coolant cooled by the other end wall portion 10c is discharged upward through the exhaust portion coolant outlet connection portion 72d by cooling the portion of the exhaust portion coolant flow path 72 located near the exhaust port 55 located at the lower portion of the other end wall portion 10c with the coolant cooled by the coolant inlet 72 b. At this time, the cooling liquid undergoes heat exchange to increase in temperature, and the specific gravity thereof decreases, thereby generating a vector of upward flow. According to this flow of the coolant, the portion of the lower exhaust port 55 can be cooled effectively, and the directionality of the flow caused by the temperature increase of the coolant can be made uniform with the directionality of the flow for discharging the coolant upward. Therefore, the coolant can be smoothly passed, and the cooling efficiency can be effectively improved.

In this case, the exhaust portion coolant flow passage 72 is provided by disposing the first flow passage forming portion 61 on the other end wall portion 10c of the pump chamber main body 110, and the first flow passage forming portion 61 includes a coolant flow passage forming surface 61a, and the coolant flow passage forming surface 61a is disposed so as to cover the outer surface side of the other end wall portion 10c and is provided so as to form the exhaust portion coolant flow passage 72 between the outer surface of the other end wall portion 10 c. This allows the exhaust portion coolant flow field 72 to be efficiently and reasonably configured.

As shown in fig. 13, 20, and 21, the first flow passage forming portion 61 of this embodiment is provided by a plate-like member having concave and convex portions formed on both surfaces thereof, and is fixed to the outer surface of the other end wall portion 10c by bolts, and the joint portion is watertight sealed by a sealing member 65 to form an exhaust portion coolant flow passage 72. The joint portion of the present embodiment is constituted by an inner ring joint portion 61c and an outer ring joint portion 61d, the inner ring joint portion 61c being formed in a rectangular annular frame shape surrounding the exhaust port 55 so as to extend the exhaust path of the exhaust port 55, and the outer ring joint portion 61d being formed in a circumferential frame shape to abut against the peripheral edge portion of the other end wall portion 10 c. Then, the following modes are obtained: an exhaust portion coolant flow passage 72 is formed between the inner ring joint portion 61c and the outer ring joint portion 61d, and is filled with coolant. This results in the following modes: the outer wall surface of the other end wall portion 10c can be cooled efficiently by bringing the coolant into contact with the entire surface. In addition, this structure is compact in structure in which the layered exhaust portion coolant flow passage 72 is stacked in a planar manner outside the outer end surface of the pump chamber main body 110.

In the first channel forming unit 61 of this embodiment, the following configuration is provided: a passage forming wall constituting the coolant flow restriction portion 61b is formed to protrude from a coolant flow passage forming surface 61a that is a surface (opposite surface) facing the outer surface of the other end wall portion 10c so as to form an exhaust port peripheral flow passage portion 72c that is a groove-like passage and is a part of the exhaust port coolant flow passage 72. That is, in this embodiment, the outer surface of the other end wall portion 10c is a flat surface, and as shown in fig. 13 and 20, a passage forming wall (coolant flow restriction portion 61 b) for guiding the exhaust portion coolant flow passage 72 to be curved appropriately is provided on the coolant flow passage forming surface 61a side of the first flow passage forming portion 61. The present invention is not limited to this, and a passage forming wall may be provided on the outer surface side of the other end wall portion 10c as appropriate.

In this case, the exhaust passage 56 through which the exhaust gas passes is provided on the side of the exhaust passage forming surface 61e, which is the outer surface of the first passage forming portion 61, on the surface of the first passage forming portion 61 opposite to the coolant passage forming surface 61a, so that the exhaust gas is cooled by the first passage forming portion 61. That is, the exhaust passage 56 is a passage connected to the exhaust port 55, and is a passage through which exhaust gas discharged from the exhaust port 55 flows.

According to the exhaust passage 56, the overheated exhaust gas can be cooled effectively, the temperature of the exhaust gas can be reduced, the temperature in the pump chamber 10 can be reduced, and overheat and thermal expansion of the constituent members forming the pump chamber body 110 and the two rotors 30A and 30B of the pump chamber 10 can be suppressed uniformly.

The exhaust passage 56 is configured to properly restrict the flow direction of the exhaust gas, promote cooling of the exhaust gas, and reduce noise of the exhaust gas. That is, the first muffler portion 31 is constituted by a structure in which the exhaust passage 56 is formed. Further, 57 is an exhaust port of the first muffler portion, is provided to be opened in an upper wall portion of the first flow path forming portion 61, becomes an exhaust port of the exhaust flow path 56, and is exhausted to the outside through the exhaust port 57 of the first muffler portion. As shown in fig. 21, the exhaust port 57 of the first muffler section of this embodiment is formed in a shape in which the flow path is reduced in diameter on the inner side, and is formed so that the noise reduction effect can be improved.

In this case, the exhaust passage 56 is provided by disposing the second passage forming portion 62 in the first passage forming portion 61, and the second passage forming portion 62 includes an exhaust passage forming surface 62a, and the exhaust passage forming surface 62a is disposed so as to cover the outer surface side of the first passage forming portion 61 and is provided so as to form the exhaust passage 56 between the outer surface of the first passage forming portion 61 and the exhaust passage forming portion. This allows the exhaust passage 56 to be effectively and reasonably configured, and allows the exhaust gas just after the exhaust port to be effectively cooled on both the exhaust passage forming surface 61e and the exhaust passage forming surface 62 a. In addition, this structure is compact in structure in which the layered exhaust flow path 56 is stacked in a plane outside the outer end surface of the pump chamber main body 110.

As shown in fig. 13 and the like, the second flow path forming portion 62 of this embodiment is provided by a disk-shaped member having an exhaust flow path forming surface 62a formed flat as an inner surface (surface abutting against the outer surface side of the first flow path forming portion 61), and is fixed to the outer surface (exhaust flow path forming surface 61 e) side of the first flow path forming portion 61 by bolts. Further, the exhaust passage forming wall 61f is provided so as to protrude from the outer surface (the exhaust passage forming surface 61 e) side of the first passage forming portion 61 with respect to the exhaust passage forming surface 62a (flat surface) to form a groove-like passage that becomes the exhaust passage 56. The annular frame-shaped joint portion 61g or the inner surfaces of the exhaust passage forming wall 61f and the second passage forming portion 62, which are the outer peripheral portions on the outer surface side of the first passage forming portion 61, can be brought into a substantially airtight state by being fixed in close contact with each other, or a sealing member is provided to bring about an airtight state. The present invention is not limited to this, and an exhaust passage forming wall may be provided on the exhaust passage forming surface 62a side. As shown in fig. 21, the exhaust passage 56 is formed as a complicated curved passage, and thus can further promote cooling of the exhaust gas, and can appropriately function as a muffler chamber, thereby further reducing exhaust sound.

Further, according to the present embodiment, the extension portion coolant flow path 73 continuous with the exhaust portion coolant flow path 72 is provided by disposing the third flow path forming portion 63 in the second flow path forming portion 62, and the third flow path forming portion 63 is provided with an extension flow path forming surface 63a, and the extension flow path forming surface 63a is a portion disposed so as to cover the outer surface (extension flow path forming surface 62 b) side of the second flow path forming portion 62, and is provided so as to form the extension portion coolant flow path 73 between the extension portion coolant flow path and the outer surface (extension flow path forming surface 62 b) of the second flow path forming portion 62. This allows the extension coolant flow field 73 to be efficiently and reasonably configured. In addition, this structure is compact in structure in which the layered extension coolant flow passage 73 is stacked in a plane outside the outer end surface of the pump chamber main body 110. Further, according to the layered extension coolant flow path 73 and the structural wall constituting the extension coolant flow path 73, noise can be reduced. That is, the structure in which the extension portion coolant flow field 73 and the exhaust portion coolant flow field 72 are formed is a structure for shielding sound and reducing noise, and is also a constituent element of the first muffler portion 31.

As shown in fig. 13 and the like, the third flow channel forming portion 63 of the present embodiment is provided by a flat plate-like member (plate-like member) that is fixed to the outer surface side of the second flow channel forming portion 62 by bolts, and is water-tightly sealed to a peripheral joint portion 62c provided in an annular frame shape on the outer surface of the second flow channel forming portion 62 by a seal member 65, thereby forming the extension portion coolant flow channel 73. In the present embodiment, the extension coolant flow path 73 is formed in a flat layered space, but the present invention is not limited to this, and the flow path may be formed appropriately. Further, the extension coolant flow path 73 may be multilayered, and the cooling performance may be improved. In the extension coolant flow path 73, an extension coolant outlet connection portion 73b is provided in an upper portion of the extension coolant flow path 73 so as to communicate with an extension coolant inlet connection portion 73a provided in a lower portion of the second connection pipe 72e from an exhaust coolant outlet connection portion 72d provided in an upper portion of the second connection pipe 72e and connected to the exhaust coolant flow path 72 via the second connection pipe 72e, and so as to discharge the coolant flowing through the extension coolant flow path 73 to the outside, and so as to cause the coolant to flow from the lower portion to the upper portion in the same manner as the exhaust coolant flow path 72.

In this case, the pump chamber 10 is formed by fixing the cylinder case 11 and the side plate 12 provided as the other end wall portion 10c in a sealed state, and the cylinder case 11 is integrally provided with the cylinder portion 10a and one end wall portion 10b and one structural wall portion 121a provided with the first bearing portion 40 a. In this way, in the present embodiment, the pump chamber 10 is formed of a member divided into two, but not limited to this, and may be formed of a member mainly divided into three, for example, the cylinder portion 10a, one end wall portion 10b, and the other end wall portion 10 c.

Next, a configuration example of the bearing portion 40 for supporting the two rotary shafts 20A and 20B by cooling the biaxial rotary pump according to the present invention will be described in detail with reference to the drawings (fig. 13 to 21). As described above, the biaxial rotary pump of the present embodiment is a package type rotary pump unit, but the present invention is not limited to this, and can be applied to other biaxial rotary pumps such as a roots pump and a screw pump. The biaxial rotary pump according to the present invention is not limited to the configuration in which the two rotors 30A and 30B are supported and supported in a cantilever state, and the present invention is applicable to a biaxial rotary pump in which the rotary shafts 20A and 20B are rotatably supported at both ends.

As shown in fig. 13, the biaxial rotary pump of the present invention includes a bearing body 120, and the bearing body 120 constitutes a structural wall 121, and the structural wall 121 includes a bearing 40 that pivotally supports the two rotary shafts 20A and 20B, and a gear case 45 is provided with a pair of gears 21A and 21B that are provided in correspondence with and mesh with the two rotary shafts 20A and 20B, and the gear case 45 is incorporated. The bearing body 120 of this embodiment is provided with a bearing portion 40 for pivotally supporting the rotary shafts 20A and 20B such that the two rotors 30A (driving-side rotors) and 30B (driven-side rotors) are respectively disposed at one ends of the two rotary shafts 20A (driving-side rotary shafts) and 20B (driven-side rotary shafts) and supported in a cantilever state. The bearing body 120 and the pump chamber body 110 constitute a pump body 100 of the biaxial rotary pump.

The pump body 100 is provided so as to be divided into the pump chamber body 110 and the bearing body 120, and a bearing portion coolant flow path 71 for passing coolant is provided in a structure wall portion 121 (in this case, one structure wall portion 121 a) of the bearing body 120 on the pump chamber body 110 side so that a cooling gap 60 capable of suppressing heat conduction is formed between the pump chamber body 110 and the bearing body 120.

This reduces the heat transfer preventing effect of the compressed gas (exhaust gas) heat transferred to the bearing body 120 by the driving of the two rotors 30A and 30B and the cooling effect of the coolant passing through the bearing coolant flow path 71, thereby providing a particularly advantageous effect of being able to extend the life of the functional components constituting the bearing 40 and the like. That is, according to the present invention, by dividing the pump chamber main body 110 and the bearing main body 120 and providing the cooling gap 60, heat conduction can be suppressed to minimize the heat transfer amount, and the bearing main body 120 can be cooled more positively by the coolant passing through the bearing portion coolant flow path 71, so that the reliability of the apparatus can be improved. In this example, it was confirmed that the temperature of the lubricating oil could be raised and lowered by about 40 ℃.

The functional component is a component including the bearing 41 and the oil seal 42, and is handled as a consumable component. By realizing a longer life of these functional components, the running cost can be reduced.

The bearing 40 of this embodiment is composed of a first bearing 40A and a second bearing 40B, the first bearing 40A is provided on the pump chamber main body 110 side structure wall (one structure wall 121A) of the bearing main body 120 so as to pivotally support the two rotary shafts 20A, 20B between the two gears 21A, 21B and the two rotors 30A, 30B, and the second bearing 40B is provided on the opposite structure wall to the first bearing 40A and is disposed on the structure wall (the other structure wall 121B) on the side where the drive motor (electric motor 3 (see fig. 3, etc)) is connected to. The rotation shaft 3a of the electric motor 3 is coupled to a coupling 3b (see fig. 4, etc.) via a rotation shaft 20A (drive-side rotation shaft).

In this case, the two rotating shafts 20A and 20B are horizontally arranged so as to be horizontally arranged, and the bearing portion cooling liquid passage 71 is provided below the structure wall portion 121 of the bearing main body portion 120 so as to pass below the liquid surface of the lubricating oil in the storage state at rest, thereby cooling the lubricating oil stored in the gear case 45. The liquid level at the time of the lubrication oil standing still is set to be located between the inner bottom surface of the gear case 45 (oil chamber) and the horizontally arranged rotating shafts 20A and 20B. This effectively cools the lubricating oil, and the gears 21A and 21B and the bearings 41 can be lubricated by the lubricating oil lifted up by the rotating two gears 21A and 21B, and the inside of the gear case 45 can be cooled.

In this case, the following forms are used: the bearing portion coolant flow field 71 is provided in the bearing main body portion 120 in the shape of a straight through hole in the lower portion of the first bearing portion 40a (the lower side of the bearing 41 of the first bearing portion 40 a), and is partially disposed. This has the following effects: the portion of the bearing main body portion 120 that is susceptible to heat conduction from the pump chamber main body portion 110 side is actively cooled, and the lubricating oil can be effectively cooled.

Further, in this embodiment, the exhaust port 55 of the pump chamber 10 is provided at the lower portion of the pump chamber body 110. Accordingly, when the bearing portion coolant flow field 71 is provided in the lower portion of the structural wall portion 121 of the bearing main body portion 120 as described above, heat conduction is effectively suppressed, and overheating of the bearing portion 40 can be suppressed.

In addition, instead of arranging the two rotation shafts 20A and 20B horizontally to be horizontal as in the present embodiment, an air blowing means for causing air to flow so as to escape from the lower side to the upper side may be provided in the cooling gap 60. This effectively cools the pump chamber main body 110 and the bearing main body 120, and further improves the reliability of the biaxial rotary pump. That is, since the cooling air can appropriately flow between the pump chamber main body 110 and the bearing main body 120, heat transfer can be suppressed more effectively, and cooling by heat dissipation can be promoted. This can suppress the temperature rise of the bearing main body 120, and can lengthen the life of the functional component.

Further, according to the biaxial rotary pump of the present invention, the bearing portion coolant flow passage 71 is connected to the coolant flow passage provided in the pump chamber main body portion 110, so that the pump chamber main body portion 110 is cooled by the coolant that cools the bearing main body portion 120. As a result, the temperature of the coolant flowing through the bearing portion coolant flow path 71 so as not to boil and overheat the lubricating oil can be made lower than the temperature of the coolant flowing through the coolant flow path provided in the pump chamber main body 110, and the coolant can be effectively used.

In this case, the bearing portion coolant flow field 71 is connected to the exhaust portion coolant flow field 72 so that the coolant flows in the order from the bearing portion coolant flow field 71 to the exhaust portion coolant flow field 72. As a result, the structure wall portion 121 (one structure wall portion 121 a) of the bearing portion 40 (first bearing portion 40 a) of the bearing main body portion 120 and the other end wall portion 10c side of the pump chamber main body portion 110 can be directly and sequentially cooled by the single coolant supply source 4 (fig. 1 and 2). The coolant in this embodiment is supplied from the coolant supply source 4 (fig. 1 and 2), flows through the coolant inlet connection 71a (fig. 15, 17, and 19), the bearing coolant flow field 71 (fig. 13 and 19), and the bearing coolant outlet connection 71b (fig. 14, 16, 18, and 19), flows through the first connection pipe 71c (fig. 14, 16, 18, and 19), the exhaust coolant inlet connection 72a (fig. 14, 16, and 18), and the coolant inlet 72b (fig. 20), flows through the exhaust coolant flow field 72 (fig. 13 and 20), and is discharged to the outside of the pump 2 through the extension coolant flow field 73. The present invention is not limited to this, and it is needless to say that the bearing portion cooling liquid flow path 71 and the exhaust portion cooling liquid flow path 72 may be not connected to each other, and the cooling liquid may be supplied separately or may be optimized by independently adjusting the supply of the cooling liquid.

In the present embodiment, the flow paths including the bearing portion cooling liquid flow path 71, the exhaust portion cooling liquid flow path 72, and the extension portion cooling liquid flow path 73 are configured such that the exhaust portion cooling liquid flow path 72 is disposed above the bearing portion cooling liquid flow path 71, and the cooling liquid flows from the bottom to the top in the exhaust portion cooling liquid flow path 72 and the extension portion cooling liquid flow path 73, whereby the cooling liquid can smoothly flow and the bearing portion 40 and the exhaust gas can be cooled effectively by making the flow directionality of the cooling liquid flow caused by the temperature rise and the flow directionality of the cooling liquid uniform.

According to the cooling structure of the biaxial rotary pump described above, the cooling performance can be improved appropriately for the package type rotary pump unit, and the pump performance can be improved. In the package-type rotary pump unit according to the present invention, the lower side of the pump chamber 10 is easily overheated and can be cooled from the lower side as described above. Therefore, the pump chamber 10 can be cooled efficiently, the pump performance can be improved, and the above-described advantageous effect that the lifetime of the functional components can be prolonged can be obtained.

In this case, as shown in fig. 13 to 19, the cooling gap 60 between the pump chamber main body 110 and the bearing main body 120 is formed by integrating one end wall 10b and one structural wall 121a of the first bearing 40a facing the one end wall 10b with a plurality of columnar portions 115, and the cooling gap 60 is formed in a portion where the columnar portion 115 is not provided. In this shape, for example, in the case of manufacturing by casting molding, the cooling gap 60 may be formed by a core. It should be noted that the present invention is not limited thereto, and as shown in fig. 22, the pump chamber main body 110 side member including one end wall portion 10b and the bearing main body 120 side member constituting the structure wall portion 121 of the bearing portion 40 facing the one end wall portion 10b may be configured by different members and may be connected by columnar connection portions 111 and 122 formed in both sides, so that the cooling gap 60 may be formed.

In addition to the above-described configuration, in the sealed rotary pump unit according to the present invention, the exhaust port 50 provided at the position of at least one of the end wall portion 10B and the other end wall portion 10c facing the portion where the gas in the pump chamber 10 is compressed may be provided through the front-stage vent port 51 and the rear-stage vent port, the front-stage vent port 51 being in communication with the outside of the pump chamber 10 at the front stage where the compression ratio of the gas is maximized by the claw portions of the two rotors 30A and 30B, and the rear-stage vent port being in communication with the outside of the pump chamber 10 at the stage where the compression ratio of the gas is maximized by the claw portions of the two rotors 30A and 30B, the rear-stage vent port being in communication with the outside of the pump chamber 10 at the exhaust port 55 provided at the other end wall portion 10c, and the front-stage vent port 51 being closed by the rotors.

This can prevent reverse flow of exhaust gas, suppress overheating of the pump chamber 10, and improve pump performance. By the multiplication effect of the reverse flow prevention effect of the exhaust gas and the cooling effect of the coolant described above, overheating of the pump chamber 10 can be prevented more effectively, and the pump performance can be improved.

In this case, the two rotors 30A and 30B are supported in a cantilever state, but the present invention is not limited to this, and is also applicable to a package type rotary pump unit having a structure in which the two rotors 30A and 30B are supported from both sides by two rotary shafts 20A and 20B as disclosed in patent document 1. Further, the present invention can be effectively applied to a sealed rotary pump unit including exhaust ports in both one end wall portion and the other end wall portion of a pump chamber main body as disclosed in patent document 1, and the exhaust port coolant flow passage may be provided in one end wall portion side in addition to the balance with the exhaust port coolant flow passage provided in the other end wall portion side.

In the present invention, for example, the temperature of the coolant can be adjusted and controlled to correspond to the use in a cold region, and the scope of the present invention can be widened, or the coolant can be cooled by using a heat exchanger to circulate the coolant, or the like.

While the present invention has been described above by way of examples of suitable embodiments, the present invention is not limited to the examples, and it is needless to say that many modifications can be made without departing from the spirit of the invention.

Symbol description

1-a sealed case, 1A-a case frame part, 1B-a base part, 1 c-a case cover part, 2-a rotary pump, 3-an electric motor, 3 a-a rotary shaft, 3B-a coupling, 3 c-a safety cover, 4-a coolant supply source, 4 a-a coolant supply connection port, 4B-a coolant supply pipe, 4 c-a coolant discharge pipe, 4 d-a coolant discharge connection port, 5-a liquid cooling heat exchanger, a 5 a-heat exchange pipe, 5B-a coolant connection pipe, 6-a blower device, 7-a blower fan, 8-a distributor, 9-a blower for electric component cooling, 10-a pump chamber, 10A-a cylinder part, 10B-one end wall part, 10 c-the other end wall part, 11-a cylinder case, 12-a side plate, 14-an air suction connection port, 15-an air suction port, 16-air suction inlet connection port, 17-check valve, 20A-a rotary shaft (driving side rotary shaft), 20B-a rotary shaft (driven side rotary shaft), 21A-a gear (driving side gear), 21B-a gear (driven side gear), 25-a pump cover portion, 25 a-a circulating air inlet portion, 25B-a circulating air outlet portion, 30A-a rotor (driving side rotor), 30B-a rotor (driven side rotor), 31-a first muffler portion, 32-a second muffler portion, 33-a vibration damping pipe, 34-an exhaust gas introduction port of the second muffler portion, 35-an exhaust gas discharge port of the second muffler portion, 37-a hanging member, 40-a bearing portion, 40A-a first bearing portion, 40B-a second bearing portion, 41-a bearing, 42-an oil seal, 45-a gear case, 50-an exhaust side opening portion, 51-a front stage air vent, 55-exhaust port, 56-an exhaust passage, 57-an exhaust gas discharge port of the first muffler portion, 60-a gap for cooling, 61-a first flow passage forming portion, 61 a-a coolant flow passage forming surface, 61 b-a coolant flow restriction portion, 61 c-an inner ring joining portion, 61 d-an outer ring joining portion, 61 e-an exhaust flow passage forming surface, 61 f-an exhaust flow passage forming wall, 61 g-an annular frame-like joining portion, 62-a second flow passage forming portion, 62 a-an exhaust flow passage forming surface, 62 b-extended flow path forming surface, 62 c-peripheral joint portion, 63-third flow path forming portion, 63 a-extended flow path forming surface, 65-sealing member, 71-bearing portion coolant flow path, 71 a-coolant inlet connection portion, 71 b-bearing portion coolant outlet connection portion, 71 c-first connection piping, 72-exhaust portion coolant flow path, 72 a-exhaust portion coolant inlet connection portion, 72 b-coolant inlet, 72 c-exhaust port peripheral flow path portion, 72 d-exhaust portion coolant outlet connection portion, 72 e-second connection piping, 73-extension portion coolant flow path, 73 a-extension portion coolant inlet connection portion, 73 b-extension portion coolant outlet connection portion, 81-operation portion, 82-electric component, 83-inverter, 90-condensate water discharge connection port, 91-drain pan, 92-condensate water piping, 93-heat exchanger drain pan, 94-heat exchanger condensate water piping, 100-pump body, 110-pump chamber body portion, 115-columnar portion, 120-bearing body portion, 121-structural wall portion, 121 a-one structural wall portion, 121 b-the other structural wall portion, 200-electric rotary pump, 300-vibration damping member.

Claims

1. A packaged rotary pump unit is provided with: an electric rotary pump provided with a rotary pump for sucking/discharging gas and an electric motor for driving the rotary pump; and a sealed case in which the electric rotary pump is incorporated, wherein the sealed rotary pump unit includes:

a liquid-cooled heat exchanger disposed inside the sealed case and cooled by receiving a supply of a cooling liquid from a cooling liquid supply source disposed outside the sealed case; and

a blower device which is disposed in the sealed case and which feeds the internal air in the sealed case including the heated air generated by heating the air around the rotary pump by the operation of the rotary pump to the liquid-cooled heat exchanger to cool the internal air,

the rotary pump is a biaxial rotary pump in which one rotor rotation shaft is connected in series to the rotation shaft of the electric motor and rotates, and the other rotor rotation shaft rotates in synchronization with the one rotor rotation shaft via a gear, and the liquid-cooled heat exchanger and the blower are disposed in a space on an extension line where the shaft center of the other rotor rotation shaft is disposed, that is, in a space adjacent to a portion where the electric motor and the one rotor rotation shaft are connected.

2. The rotary pump unit of claim 1, wherein,

the rotary pump is provided with a pump cover part which is arranged in the sealed box body and covers the rotary pump, and is formed by the following steps: a circulating air inlet portion for introducing the internal air circulating inside the sealed case; and a circulating air outlet portion that discharges the internal air including the heated air.

3. The rotary pump unit of claim 2, wherein,

the liquid-cooled heat exchanger is connected to the circulating air outlet portion side,

the air supply device is connected to the liquid-cooled heat exchanger to suck the internal air, and the internal air flows from the circulating air inlet portion to the circulating air outlet portion and passes through the liquid-cooled heat exchanger.

4. The rotary pump unit of claim 1, wherein,

the electric motor is provided with an air-blowing fan for cooling the electric motor to blow air to the electric motor, and the air-blowing fan is arranged at a side opposite to a side connected to the one rotor rotating shaft to blow air to the motor main body.

5. The rotary pump unit of claim 1, wherein,

the rotary pump is connected to the coolant supply source to be cooled.

6. The rotary pump unit of claim 1, wherein,

the pump cover part is provided with a pump cover part,

the pump cover part is arranged in the sealed box, is arranged to cover the periphery of the rotary pump except the electric motor in the electric rotary pump, and is formed by the following steps: a circulating air inlet portion for introducing the internal air circulating inside the sealed case; a circulating air outlet portion for discharging the internal air including the heated air,

the circulating air inlet is provided to surround the rotary pump and is opened in a band shape.

7. The rotary pump unit of claim 6, wherein,

the rotary pump includes a bearing main body portion, a pump chamber main body portion, and a first muffler portion,

the pump cover portion is provided to cover the periphery of the bearing main body portion and the pump chamber main body portion.

8. The rotary pump unit of claim 7, wherein,