CN115768984A - Packaged rotary pump unit - Google Patents

Abstract

The invention provides a sealed rotary pump unit, which can prevent the internal air of a sealed box body from overheating even if a rotary pump arranged in the sealed box body is used as a vacuum pump in a range with high vacuum degree, thereby maintaining high pump performance and prolonging the service life of the device. The sealed rotary pump unit includes: an electric rotary pump (200) provided with a rotary pump (2) for sucking and discharging gas and an electric motor (3); and a sealed box (1) in which the electric rotary pump (200) is built, and which is provided with: a liquid-cooled heat exchanger (5) which is disposed inside the sealed casing (1), and which is cooled by being supplied with a coolant from a coolant supply source (4) disposed outside the sealed casing (1); and a blower device (6) which is disposed inside the sealed box (1) and which cools the internal air in the sealed box (1) by sending the internal air to the liquid-cooled heat exchanger (5), the internal air including heated air generated by heating the air around the rotary pump (2) by the operation of the rotary pump (2).

Description

Packaged rotary pump unit

Technical Field

The present invention relates to a packaged rotary pump unit, including: an electric rotary pump including 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 built.

Background

As a conventional package type rotary pump unit, the present applicant has proposed an exhaust gas temperature adjusting system of an air pressure device station, characterized in that an air pressure device, a storage box, an air blowing device, a water-cooled cooler, and at least one of a water temperature control unit and a flow rate control unit are provided, the air pressure device being a device that generates air pressure of negative pressure or positive pressure such as a vacuum pump or a blower, the storage box being capable of storing a plurality of the air pressure devices and being capable of insulating sound by storing the air pressure device in a closed space, the air blowing device generating a cooling air flow flowing substantially from below to above in the storage box for cooling the storage box heated by the air pressure device in order to suck in outside air, and discharging the cooling air flow, the water-cooled cooler being provided for cooling the cooling air flow therethrough, the cooling unit supplying cold water to the cooler, the water temperature control unit controlling water temperature to adjust temperature of the cold water supplied to the cooler, the flow rate control unit controlling flow rate to adjust flow rate of the cold water supplied to the cooler, and the flow rate control unit controlling flow rate of the cold water supplied to the cooler, the air flow rate being provided in the middle of the air pressure portion in a height direction, and the shelf-supported portion being provided with a shelf-supported portion for allowing the air flow (see patent document).

As an example of a rotary pump incorporated in a package-type rotary pump unit, as shown in fig. 22, the present applicant has 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 a part of two circles are overlapped, and including: two rotating shafts 20A, 20B which are arranged in parallel in the pump chamber 10 and rotate at the same speed in opposite directions; two rotors 30A and 30B which are provided on the two rotary shafts 20A and 20B, respectively, are arranged in the pump chamber 10, and have hook-shaped claws formed thereon so as to be rotatable in a state where they do not contact each other, and which compress and discharge the sucked gas; and an exhaust side opening portion 50 provided at a position facing a portion of the pump chamber 10 where the gas is compressed, at least one of the one end wall portion 10B and the other end wall portion 10c, wherein the exhaust side opening portion 50 is provided by a front stage vent port 51 and a rear stage exhaust port (exhaust port 55), the front stage vent port 51 communicates with the outside of the pump chamber 10 at a front stage where the gas compression ratio is maximized by the claw portions of the two rotors 30A and 30B, the rear stage exhaust port (exhaust port 55) communicates with the outside of the pump chamber 10 at a stage where the gas compression ratio is maximized, the front stage vent port 51 is closed by the rotor bearing portion 30A, a gaps for cooling are formed between the pump chamber main body portion and the bearing main body portion, the pump body is provided with a bearing portion 20B of the cylinder 10 and a bearing portion 20B of the two end walls of the pump chamber 10, and the cylinder 10B, and the bearing portion 20B are provided in a state where the two bearing portions are supported by the rotary shaft portions 20B, respectively, and the rotary shaft portion 20B of the rotary shaft portion of the rotary shaft cylinder 10.

According to the claw pump proposed by the applicant, the exhaust side opening portion 50 is constituted by a front stage vent hole 51 and a rear stage exhaust port (exhaust port 55) which are opened, respectively. Therefore, for example, when the vacuum pump is used in a high vacuum state, the front stage vent port 51 draws in non-overheated outside air into the pump chamber 10, whereby reverse flow of exhaust gas can be suppressed at the rear stage exhaust port (exhaust port 55), and overheating of the pump chamber 10 can be prevented, thereby improving the pump performance.

Documents of the prior art

Patent document

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

Patent document 2: japanese patent No. 6749714 (claim 1, FIG. 3)

Disclosure of Invention

Problems to be solved by the invention

The problem to be solved by the enclosed rotary pump unit is that, in the conventional enclosed rotary pump unit, although it is proposed to introduce cooling air from the outside and discharge the air heated by the rotary pump to the outside of the casing, no consideration is given to effectively preventing overheating in the sealed casing when the rotary pump is built 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 in the sealed case is increased due to overheating caused by the operation of the rotary pump, the electric motor, the electric components, and the like are adversely affected, and therefore, appropriate temperature measures are required.

Accordingly, an object of the present invention is to provide a packaged rotary pump unit capable of preventing overheating of the air inside a sealed casing, maintaining high pump performance, and extending the life of the device, even when a rotary pump built in the sealed casing generates a large amount of heat when used as a vacuum pump in a range of high vacuum degree, 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 canned rotary pump unit comprising: an electric rotary pump including 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 built, and the sealed rotary pump unit includes: a liquid-cooled heat exchanger disposed inside the sealed casing and cooled by receiving a supply of a coolant from a coolant supply source disposed outside the sealed casing; and an air blowing device that is disposed inside the sealed case and that blows the internal air in the sealed case containing heated air to the liquid cooling heat exchanger to cool the internal air, wherein the heated air is generated by heating air around the rotary pump by operation of the rotary pump, the rotary pump is a two-shaft rotary pump, one rotor rotating shaft is connected in series to a rotating shaft of the electric motor to rotate, the other rotor rotating shaft rotates synchronously in a direction opposite to the one rotor rotating shaft via a gear, and the liquid cooling heat exchanger and the air blowing device are disposed in a space on an extension line of an axis of the other rotor rotating shaft, that is, a space adjacent to a portion where the electric motor and the one rotor rotating shaft are connected.

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

In addition, according to an aspect of the packaged rotary pump unit of the present invention, the liquid-cooled heat exchanger may be connected to the circulating air outlet portion side, and the air blowing device may be connected to the liquid-cooled heat exchanger to suck the internal air and cause the internal air to flow from the circulating air inlet portion to the circulating air outlet portion and to pass through the liquid-cooled heat exchanger.

In addition, according to an aspect of the packaged rotary pump unit 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 including: an electric rotary pump including 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 built, wherein the sealed rotary pump unit includes: a liquid-cooled heat exchanger disposed inside the sealed casing and cooled by receiving a supply of a coolant from a coolant supply source disposed outside the sealed casing; and an air blower device which is disposed inside the sealed casing and which blows internal air in the sealed casing containing heated air to the liquid-cooled heat exchanger to cool the internal air, wherein the heated air is generated by heating air around the rotary pump by operation of the rotary pump, and a liquid-cooled flow path from the coolant 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 coolant from the coolant supply source which cools the liquid-cooled heat exchanger.

In addition, according to an aspect of the packaged rotary pump unit of the present invention, the rotary pump may include a bearing main body portion, a pump chamber main body portion, and a first muffler portion, and the liquid cooling passages from the coolant supply source may be connected in series so that the coolant from the coolant 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 packaged rotary pump unit of the present invention, the electric motor may be provided with an electric motor cooling air blowing fan for blowing air to cool the electric motor, and the air blowing fan may be disposed on a side opposite to a side connected to the one rotor rotation shaft and configured to blow air to the motor main body.

Effects of the invention

According to the encapsulated 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 or when the rotary pump incorporated in the sealed casing generates a large amount of heat when used as a vacuum pump in a range of high vacuum degree, for example, the internal air of the sealed casing can be prevented from being overheated, so that high pump performance can be maintained and the service life of the apparatus can be prolonged.

Drawings

Fig. 1 is a block diagram schematically showing a flow of a liquid coolant and a flow of a circulating gas (air) inside a sealed casing in an example of a sealed rotary pump unit according to the present invention.

Fig. 2 is a block diagram schematically showing the flow of the liquid and the flow of the exhaust gas in an embodiment 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 of the encapsulated rotary pump unit according to the present invention.

Fig. 4 is a perspective view showing a state where the pump cover portion of the example of fig. 3 is removed.

Fig. 5 is a plan view of the electric rotary pump mounted in the example of fig. 3.

Fig. 6 is a plan view showing a state where the pump cover portion of the example of fig. 5 is removed.

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

Fig. 8 is a perspective view showing an external appearance of a case in which two electric rotary pumps of the package type rotary pump unit of the present invention are housed in upper and lower stages.

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

Fig. 10 is a side view showing an internal structure of the hermetic container in the example of fig. 8.

Fig. 11 is a perspective view showing the internal structure of the sealed box of the example of fig. 8, with the distribution board removed.

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

Fig. 13 is a sectional perspective view showing a state of being cut in a stepped manner in order to show an internal structure of a configuration example of a rotary pump (claw pump) mounted on a package type rotary pump unit of the present invention.

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 square case of fig. 13.

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

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

Fig. 19 is a cross-sectional perspective view showing a bearing portion cooling liquid flow path in the example of fig. 13.

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

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

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

Detailed Description

Hereinafter, an example of a configuration example of the packaged 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 with reference to the drawings (fig. 1 to 21). The rotary pump of the present invention is a vacuum pump, and is a water-cooled double-shaft 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 for a blower or the like that uses discharged gas as product gas, a pump including a single-shaft rotary pump such as a vane pump, or a pump that uses water or other liquid coolant.

The package type rotary pump unit of the present invention includes, as a basic configuration: an electric rotary pump 200 including a rotary pump 2 that sucks and discharges gas and an electric motor 3 that drives the rotary pump 2; and a sealed case 1 in which the electric rotary pump 200 is built.

The sealed casing 1 of the present invention does not need to be sealed by strictly airtight sealing, and may be a casing that forms a closed space that sufficiently restricts the outflow/inflow of gas (air in this embodiment) between the inside of the casing and the outside, and may have a degree of tightness that is greater than or equal to a degree at which the circulation of the internal air in the sealed casing 1 is substantially free from the influence of the outside air (outside air). That is, in the sealed casing 1 of the present invention, a minute gap is allowed, and a sealing degree to a sufficient extent for restricting the circulation of air may be obtained by abutting structural members such as steel plates constituting the casing against each other, instead of using a sealing material as in the present embodiment.

The sealed casing 1 of the present embodiment has a rectangular box shape, and includes a casing frame portion 1a (see fig. 3, 9, and the like), a base portion 1b (see fig. 3, 9, and the like), and a casing cover portion 1c (see fig. 8). The sealed casing 1 is configured such that a casing cover portion 1c formed of a steel plate or the like covers a casing frame portion 1a formed of a square steel pipe, an angle steel or the like into a lattice structure.

Inside the sealed casing 1 are disposed: an electric rotary pump 200 including a rotary pump 2 and an electric motor 3, a liquid-cooled heat exchanger 5, a blower 6, a pump cover 25, a distribution board 8, a first silencer unit 31, a second silencer unit 32, a blower 9 for cooling electric components, a dew pan 91, various pipes, various electric wires, and their accessories.

Reference numeral 5 denotes a liquid-cooled heat exchanger, which is disposed inside the sealed casing 1 and is provided to receive a supply of coolant from a coolant supply source 4 disposed outside the sealed casing 1 and to be cooled, as shown in fig. 1 and 3 to 7. 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. Further, in fig. 1, the flow of the cooling liquid is schematically shown by double-line arrows.

The liquid-cooled heat exchanger 5 of this embodiment is in the form of so-called fin/tube, that is, a heat exchange pipe line 5a through which cooling liquid flows is housed in a rectangular box-shaped heat exchange chamber in a state of being wound back and forth (zigzag). In the rectangular box-shaped heat exchange chamber of the present embodiment, a rectangular inlet port, which is a side for introducing the internal air (circulating air), is connected to a circulating air outlet port 25b of a pump cover portion 25, which will be described later, and a rectangular outlet port, which is a side for discharging the internal air (circulating air), is connected to an air blower 6, which will be described later. Thereby, the fan cooler having the liquid-cooled heat exchanger 5 is constituted. Since the liquid-cooled heat exchanger 5 is of a normal type, detailed illustration thereof is omitted. As the liquid-cooled heat exchanger 5, it is needless to say that 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 selectively set as appropriate.

Here, as the cooling liquid supply source 4, a liquid cooling device that cools liquid by a refrigeration cycle can be used. In addition, depending on the site conditions and the like, other cooling sources such as air (outside air), fresh water, seawater, ice, and ground water may be used, and further, a plurality of cooling sources may be used in combination as appropriate. The coolant in this embodiment is coolant, 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.

Reference numeral 6 denotes an air blower which is disposed inside the sealed casing 1 and includes: the air inside the sealed casing 1 containing the heated air generated by heating the air around the rotary pump 2 by the operation of the rotary pump 2 is sent to the liquid-cooled heat exchanger 5 to be cooled. Further, in fig. 1, the flow of the inside air is schematically shown by thick line arrows.

The blower 6 of this embodiment is an axial fan and is arranged to suck and discharge the internal air along the longitudinal direction of the electric rotary pump 200. The air blowing device 6 is not limited to the axial flow fan, but other air blowing means such as a centrifugal fan (for example, a sirocco fan) may be used as appropriate.

According to the packaged rotary pump unit of the present invention, even when the unit is operated in a high-temperature environment or when the rotary pump 2 incorporated in the sealed casing 1 is used as a vacuum pump in a range of high vacuum degree, for example, and generates a large amount of heat, the internal air of the sealed casing 1 can be prevented from being overheated, and the following advantageous effects can be achieved: the pump performance can be maintained high, and the service life of the device can be prolonged. That is, the internal air in the sealed casing 1 is caused to flow by the blower 6 and passes through the liquid-cooled heat exchanger 5, whereby the superheated air can be prevented from stagnating around the rotary pump 2, and the internal air can be efficiently circulated and cooled. Therefore, the temperature rise in the sealed casing 1 due to heat generation of the rotary pump 2 and 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 life can be extended.

Further, since all or most of the heat released to the outside of the sealed casing 1 is released through the medium of the coolant (cooling water) for heat exchange, the heat release to the surroundings can be minimized, and there is an advantage 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 installed can be reduced.

Further, since the sealed casing 1 has a sealed structure, there is an advantage that the operation sound reduction effect is large. Further, according to the embodiment of the sealing structure of the sealed casing 1 of the present embodiment, the noise can be reduced to 73dB.

In addition, by forming the sealed structure by the sealed casing 1 in this way, inflow/outflow of 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 condensed water generated inside the casing is small. That is, if the cooling liquid can be supplied, the internal temperature of the sealed casing 1 is less likely to be affected by the product installation environment (temperature, humidity), and therefore, the sealed casing can be used in a wide range of environmental temperature and humidity.

As described later, in this embodiment, the first muffler portion 31 and the second muffler portion 32 are housed in the sealed casing 1, and the internal air of the sealed casing 1 including the heat radiated from these muffler portions can be cooled.

In this embodiment, the pump cover unit 25 is provided, and the pump cover unit 25 is disposed inside the hermetic container 1 so as to cover the rotary pump 2, and is formed so as to include: a circulating air inlet 25a for introducing the internal air circulating inside the sealed casing 1; and a circulating air outlet part 25b for discharging the internal air containing the heated air. The installation position of the blower 6 with respect to the pump cover portion 25 is not limited to this embodiment, and may be selectively set as appropriate including the positional relationship with the liquid-cooled heat exchanger 5, as long as the internal air can be introduced from the circulating air inlet portion 25a and discharged from the circulating air outlet portion 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 dissipated to the outside of the pump cover portion 25 and dispersed to the entire space inside the sealed casing 1. Thus, by preventing the heat generated by the rotary pump 2 from being dispersed, high-temperature air (heated air) can be sent to the liquid-cooled heat exchanger 5 in a concentrated state, and the heated air can be cooled efficiently. 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 casing 1 can be efficiently suppressed. Further, since the high-temperature air is sent to the liquid-cooled heat exchanger 5 in a concentrated state, the circulation air outlet portion 25b has a reduced diameter, and therefore, the liquid-cooled heat exchanger 5 can be downsized, and the product cost can be reduced.

The pump cover portion 25 of the present embodiment is provided with a circulating air inlet portion 25a that is opened in a band shape around the periphery of the rotary pump 2 on the exhaust side of the rotary pump 2 (the side opposite to the side to which the electric motor 3 is connected), so that the outer surface of the rotary pump 2 can be effectively cooled by flowing the internal air so as to effectively contact the entire outer surface thereof. The circulating air outlet 25b, which discharges the internal air including the heated air heated by the rotary pump 2, has a reduced flow path diameter, and intensively guides the internal air to the liquid-cooled heat exchanger 5. Further, in this embodiment, the circulating air outlet port 25b is connected to the inlet port of the internal air of the heat exchange chamber of the liquid-cooled heat exchanger 5 in an air-tight sealed state. This allows the flow of the inside air to be appropriately generated, the inside air to be appropriately circulated, heat exchange to be efficiently performed, and an increase in temperature in the sealed casing 1 to be efficiently suppressed.

In this embodiment, 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 pass through the liquid-cooled heat exchanger 5. In this case, the air inlet of the blower 6 is connected to the air outlet of the liquid-cooled heat exchanger 5 in the heat exchange chamber in an air-tight sealed state.

This enables the inside air to flow smoothly and efficiently, and the inside air to circulate efficiently, thereby efficiently exchanging heat and efficiently suppressing the temperature rise in the sealed casing 1. In addition, by disposing the air blowing device 6 in the liquid cooling heat exchanger 5 as in this embodiment, the air blowing device 6 itself sucks the air cooled by the liquid cooling heat exchanger 5, thereby preventing overheating and extending the life of the device.

In this embodiment, the pump cover portion 25 (see fig. 3 to 6 and the like) 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 and the like) of the rotary pump 2. That is, as described later, the portion having a high surface temperature except for the first muffler portion 31 that is cooled is effectively covered. In addition, in order to form the circulating air inlet portion 25a adaptively, the size of the gap (width of the air passage) provided between the inner surface of the pump cover portion 25 and the outer surface of the rotary pump 2 may be set in the following range: the ventilation resistance when the internal air flows is kept as low as possible, and the internal air (heated air) heated by the heat generated by the rotary pump 2 is kept as low as possible from being dispersed to the outside of the pump cover portion 25.

In this embodiment, the rotary pump 2 is a two-shaft rotary pump, and is configured such that one rotor rotating shaft (rotating shaft 20A) is connected in series to the rotating shaft 3a of the electric motor 3 and rotates, and the other rotor rotating shaft (rotating shaft 20B) synchronously rotates in the direction opposite to the one rotor rotating shaft (rotating shaft 20A) through a gear, and the liquid cooling heat exchanger 5 and the air blowing device 6 are disposed in the following space: is located on an extended line of the axial center of the rotating shaft 20B on which the other rotor rotating shaft (rotating shaft 20B) is disposed, and is adjacent to a portion where the electric motor 3 and the one rotor rotating shaft (rotating shaft 20A) are connected.

This enables the internal space of the sealed casing 1 to be appropriately utilized, and the internal air to be appropriately circulated.

As shown in fig. 4 and the like, one rotor rotating shaft (rotating shaft 20A) of the present embodiment and the rotating shaft 3a of the electric motor 3 are connected in series by a coupling 3 b. As shown in fig. 3 and the like, 3c is a safety cover that covers a connection portion including the rotary shafts (3 a, 20A) of the rotationally driven coupling 3b for safety. Further, the coupling 3b may be configured to be provided with air blowing blades coaxially with the rotary shafts (3 a, 20A) to blow air. According to the blower blade, cooling performance can be improved.

In this embodiment, the electric motor 3 is provided with an electric motor cooling blower fan 7 for blowing air to cool the electric motor 3, and the blower fan 7 is provided on the side opposite to the side connected to one of the rotor rotating shafts (rotating shaft 20A) and blows air toward the motor main body.

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

Further, in this embodiment, as shown in fig. 1, 9 and 10, a blower 9 for cooling electric components is attached to a lower portion of a distribution board 8 formed on a front surface side of the sealed case 1 as an air cooling unit for flowing air in the distribution board 8 formed in a cell shape.

According to the blower 9 for cooling the electrical components of this embodiment, air can be blown so that a part of the internal air (cooling gas) in the sealed box 1 is sucked into the distribution board 8, flows upward in the distribution board 8 from below, and is discharged from an opening in the upper part, not shown, in the distribution board 8. This makes it possible to effectively cool the electric components 82, the inverter device 83, and the like, which are highly exothermic and are disposed in the distribution board 8. The internal air discharged from distribution board 8 is sucked into pump cover portion 25 from circulating air inlet portion 25a of pump cover portion 25. As shown in fig. 9 and 10, the reference numeral 81 denotes an operation portion, and since heat generation is low, in this embodiment, the air cooling unit is not separately provided, but is disposed at a position separated from the distribution board 8.

In this embodiment, 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 cooled. In this embodiment, the pipes for the coolant flowing from the coolant supply source 4 are connected in series so that the coolant first passes through the liquid-cooling heat exchanger 5 and then cools the exhaust gas discharged from the exhaust port 55 (see fig. 13 and the like). Thus, both the liquid-cooled heat exchanger 5 and the rotary pump 2 are cooled, and the temperature rise in the sealed casing 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, and the like).

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

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

Next, as will be described later with reference to fig. 13 to 21, the coolant passing through the bearing portion coolant flow path 71 flows through the exhaust portion coolant flow path 72 to cool the exhaust gas of the rotary pump 2, and further passes through the extension portion coolant flow path 73 to cool 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 coolant can be circulated through the above flow paths to cool the liquid-cooled heat exchanger 5 and the rotary pump 2, and the coolant that cools the air inside the sealed casing 1, the lubricating oil of the rotary pump 2, and the exhaust gas is returned to the coolant supply source 4 and circulated in this embodiment. In addition, when using underground water or the like, it is needless to say that the water may flow in one direction without circulating.

Thus, the liquid cooling heat exchanger 5, the bearing portion 40 and the gear case 45 of the rotary pump 2, and the first muffler portion 31 as the exhaust portion of the rotary pump 2 can be sequentially and rationally cooled by the coolant flowing through the liquid cooling flow path connected in series across the liquid cooling heat exchanger 5 and the rotary pump 2. That is, the temperature of each part is in such a temperature relationship that the allowable temperature of the oil stored in the gear box is higher than the allowable temperature of the internal air of the hermetic case 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 box, and therefore, it is reasonable to flow the coolant in this order. That is, when the three portions are sequentially cooled, the coolant is gradually heated, but a temperature difference (temperature difference between the coolant temperature and the temperature of the portion to be cooled) that enables sufficient cooling can be maintained in each portion. In addition, the liquid cooling pipes connected in series have an advantage of cost reduction by simplifying the pipe structure.

The liquid cooling pipes are not limited to this embodiment, and may be provided in parallel. The parallel arrangement allows independent adjustment of the flow rates, and has an advantage that accurate cooling control can be achieved.

Next, specific measurement data (verification values) will be described with respect to the cooling effect in the sealed casing 1 of 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 part 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 embodiments shown in fig. 13 to 21, the internal air of the sealed casing 1 rose to 80 ℃.

In contrast, in the case where the rotary pump 2 is water-cooled and the liquid-cooled heat exchanger 5 is provided to water-cool the internal air as described above in this 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 which is discharged from the blower 6 through the liquid-cooled heat exchanger 5 and circulates through the electric motor 3 and the distribution board 8 is 45 ℃. This can 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 a pipe for intake that can be connected to the outside through the intake introduction pipe connection port 16, and to be able to intake outside air through the outside intake pipe. The check valve 17 is connected between the intake air introduction pipe connection port 16 and the intake port 15 of the rotary pump 2, and is provided to be able to restrict the flow of gas from the pump 2 to the intake air introduction pipe connection port 16.

Further, reference numeral 90 denotes a condensate discharge connection port, which is a discharge port capable of discharging condensate to the outside. The condensate drain connection port 90 is connected to the condensate receiving pan 91 disposed below the rotary pump 2 and the heat exchanger condensate receiving pan 93 disposed in the liquid-cooled heat exchanger 5 via the condensate pipe 92 and the heat exchanger condensate pipe 94, and can receive and appropriately drain the generated condensate.

Next, the noise cancellation structure of the canned 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 according to the present invention includes, as a basic configuration: 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 built.

The rotary pump 2 mounted on the package type rotary pump unit of the present invention is provided with the first muffler portion 31, and the first muffler portion 31 also serves as an exhaust gas cooling portion for cooling exhaust gas with 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 muffling the exhaust gas passing through the first muffler portion 31 is disposed above the electric rotary pump 200 inside the sealed casing 1.

According to the encapsulated rotary pump unit of the present invention, when the rotary pump 2 is incorporated in the hermetic container 1, the following advantageous effects can be obtained: the noise generated by the operation of the rotary pump 2 can be reduced more reasonably and effectively. That is, by providing the first muffler portion 31 for cooling the exhaust gas of the rotary pump 2 by the coolant and disposing the second muffler portion 32 above the electric rotary pump 200, the electric rotary pump 200 and the entirety of the mufflers (the first muffler portion 31 and the second muffler portion 32) can be effectively covered by the above-described sealed case (the sealed case 1). Therefore, the noise including the sound leaking from the muffler, the piping in the middle, and the like can be shielded and absorbed, and the silencing 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 above the electric rotary pump 200, the foot space can be suppressed. In addition, in order to improve the sound absorption performance, it is needless to say that a sound absorbing material may be attached to the inner surface of the member constituting the hermetic container 1.

In this embodiment, the second muffler portion 32 is formed of a plurality of noise reduction chambers which are arranged in series in the longitudinal direction of the hermetic container 1 in the same direction as the connection direction of the rotary pump 2 and the electric motor 3.

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, since the electric rotary pump 200 of the present embodiment is a system in which the rotary pump 2 and the electric motor 3 are connected in series, it has a laterally long shape, and the hermetic container 1 is also laterally long as in the present embodiment. Further, the second muffler portion 32 can be suitably 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, it is possible to appropriately and selectively design a form that improves the noise reduction (silencing) effect of expansion, shielding, sound absorption, and the like. For example, by adopting a configuration in which three noise reduction chambers are provided and the three chambers are arranged in series, a compact structure with high noise reduction performance can be realized.

More specifically, in this embodiment, for example, the second muffler portion 32 has an axially elongated cylindrical shape, and includes a noise reduction chamber on one end side, a noise reduction chamber in the middle portion, and a noise reduction chamber on the other end side in the longitudinal direction thereof, and noise reduction is performed by discharging the exhaust gas introduced from the exhaust pipe extended from the exhaust port 57 of the first muffler portion in the noise reduction chamber on the one end side so as to expand from the portion of the perforated pipe that becomes the tip end side of the exhaust pipe. Then, a pipe is communicated so as to convey 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 noise is reduced by expansion. Further, the exhaust gas introduced into the noise reduction chamber on the other end side is discharged to the noise reduction chamber in the intermediate portion through the vent hole of the partition wall between the noise reduction chamber on the other end side and the noise reduction chamber in the intermediate portion so as to be inverted, and the exhaust gas is discharged from the noise reduction chamber in the intermediate portion to the outside through the exhaust gas discharge port 35 of the second muffler portion while being reduced in noise by expansion.

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

Thus, by utilizing the space above the electric rotary pump 200, it is possible to have an appropriate volume with a high noise cancellation effect due to expansion, and to appropriately and easily arrange the lightweight muffler (second muffler portion 32) as compared with other structural devices. It is to be understood that sound absorbing materials may be appropriately attached to the inner surfaces of the noise reduction chambers of the second muffler portion 32 to obtain a sound absorbing effect.

In this embodiment, as shown in fig. 3, 4, 7, and 9 to 12, the electric rotary pump 200 is provided in the sealed casing 1 via a vibration damping member 300, and the first muffler unit 31 and the second muffler unit 32 are connected via a vibration damping pipe 33. That is, in this embodiment, the electric rotary pump 200 is provided on the base portion 1b in the sealed casing 1 via the damper member 300 including the vibration-proof rubber, the vibration-damping pipe 33 is connected between the exhaust port 57 of the first muffler portion and the exhaust inlet 34 of the second muffler portion, and 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 with the vibration damping member 300 and connected to the second muffler portion 32 through the vibration damping pipe 33, transmission of vibration of the electric rotary pump 200 to the sealed casing 1 side can be reduced, and vibration damping and noise reduction effects can be appropriately obtained. Further, 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 appropriately and more easily provided in the sealed casing 1.

In this embodiment, as shown in fig. 8 to 12, in a case of a packaged rotary pump unit in which the electric rotary pump 200 is mounted in multiple stages (two stages in this embodiment), the second muffler portion 32 is disposed on the rear surface side in the interior of the closed casing 1, and the distribution board 8 is disposed on the front surface side. This makes the distribution board 8 a shield portion, 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, a description will be given of a configuration example of a claw pump with reference to fig. 13 to 21.

As shown in fig. 13 and the like, in the claw pump, 110 is a pump chamber 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 parts of two circles are overlapped.

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

The two rotors 30A and 30B are disposed in the pump chamber 10 so as to correspond to the two rotary shafts 20A and 20B, and are provided with hook-shaped claws so as to be rotatable in a state of not being in contact with each other and to compress and discharge the sucked gas (see fig. 22). One end wall portion 10B of the pump chamber body 110 is located on the gear case 45 side in which the pair of gears 21A and 21B are built, and an exhaust port 55 for exhausting gas is provided in at least the other end wall portion 10c of the pump chamber body 110. This constitutes a canned rotary pump unit as one type of a two-shaft rotary pump.

In this embodiment, the two rotors 30A and 30B are supported in a cantilever manner so as to be disposed corresponding to one end (one distal end) of each of the two rotary shafts 20A and 20B, the two rotary shafts 20A and 20B are pivotally supported by the bearing 40, one end wall portion 10B of the pump chamber body 110 is located on the bearing 40 side, and the other end wall portion 10c of the pump chamber body 110 is provided with the exhaust port 55 for exhausting gas. Further, reference numeral 15 denotes an intake port, which is provided to open 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 being cut out at the corner of the upper portion of the pump chamber body 110 and extending over the upper wall portion of the cylinder portion 10a and the upper portion of one end wall portion 10 b. Further, reference numeral 14 denotes an intake connection port, which is provided such that the lower end is connected to the intake port 15 and the upper end is connected to an air compressor (not shown) via a pipe.

In the package type rotary pump unit of the present invention, the exhaust unit coolant flow path 72 for passing the coolant is provided on the other end wall portion 10c side of the pump chamber body portion 110 to cool the exhaust gas discharged from the exhaust port 55. In this case (an example of the case of using the present invention as a vacuum pump), the state where the exhaust gas is discharged from the exhaust port 55 is a state where the pump chamber 10 is open in communication with the atmosphere (air) as the outside air, and the exhaust gas is discharged to the atmosphere (air). The liquid of the coolant is represented by cooling water, but it goes without saying that a liquid other than water, such as a mixed liquid (aqueous solution) with water, oil, or the like, may be used.

According to the packaged rotary pump unit of the present invention, even when used as a vacuum pump in a range in which the ultimate vacuum degree is high, which is a value close to the absolute vacuum, overheating 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 discharge portion coolant flow path 72 on the other end wall portion 10c side of the pump chamber body portion 110, the exhaust gas just discharged from the exhaust port 55 can be efficiently cooled by the coolant. Thus, even in a vacuum pump used in a high range in which the degree of vacuum is not less than a certain level, the increase 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 the leakage of gas due to the gap can be reduced, thereby improving the pump efficiency.

Further, according to the packaged rotary pump unit of the present invention, the gap can be set small as described above, so that the ultimate vacuum degree can be further increased, and overheating can be prevented even if there is reverse flow of exhaust gas, so that the opening area of the exhaust port 55 can be set larger, and a vacuum pump with a larger process air volume can be configured.

Further, according to the canned rotary pump unit of this embodiment, the other end wall portion 10c side where the exhaust port 55 is most heated is locally and actively cooled. That is, the pump chamber body 110 in which a large temperature gradient (temperature difference) occurs is configured to preferentially cool the other wall portion 10c side around the exhaust port 55 among the wall portions of the pump chamber body 110 so as to reduce the temperature difference, thereby cooling the exhaust gas. By preventing overheating of the pump chamber 10 by cooling and exhausting in this way, it was confirmed that the internal temperature difference was reduced by about 140 ℃ in the example, and that the pump performance could be significantly improved by increasing the ultimate vacuum degree to 97 kPa. In addition, conventionally, only the operation in which the ultimate vacuum degree reaches about 90kPa is performed as a limit for performing the ultimate continuous operation, so as to avoid the contact (internal interference) between the inner wall surface of the pump chamber 10 and the two rotors 30A and 30B. In contrast, according to the present invention, the shutdown operation with a higher ultimate vacuum degree can be continuously performed.

In the canned type rotary pump unit, since the gas compression ratio is high and the gas is heated and discharged, the portion of the exhaust port 55 is most easily overheated and the portion where the other end wall portion 10c of the exhaust port 55 is formed has a higher temperature than the other portion. Then, the other part of the pump chamber body 110 is lower in temperature than the other end wall 10c. Therefore, if the entire pump chamber body 110 is cooled similarly, including the cylinder portion 10A and 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 the operating portions due to thermal expansion cannot be solved.

Further, according to this embodiment, a coolant introduction port 72b (see fig. 20) for introducing the coolant into the exhaust unit coolant flow field 72 is provided in the vicinity of the exhaust port 55, and a coolant flow restriction portion 61b for restricting the flow of the introduced coolant is provided in a portion where the exhaust unit coolant flow field 72 is formed so that the coolant first 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-like projection at a plurality of positions (two positions in the present embodiment) on the coolant flow passage forming surface 61a of the first flow passage forming portion 61 described later.

Thus, by cooling the portion (the periphery of the exhaust port 55) of the pump chamber body 110 centered on the exhaust port 55, which is the most heated portion, the exhaust gas immediately after the exhaust port is cooled, and the temperature of the periphery of the exhaust port 55 and the temperature of the exhaust gas are reduced, so that the periphery of the exhaust port 55 is uniformly prevented from being excessively heated and being deformed unevenly due to thermal expansion. In this way, thermal expansion of the pump chamber body 110 and the two rotors 30A and 30B can be suppressed in a balanced manner, and therefore, the gap between them can be reduced, and pump efficiency can be improved.

In the sealed rotary pump unit, the exhaust port 55 is usually provided at a position corresponding to a lower portion of the pump chamber 10 (in this case, a lower portion of the other end wall portion 10 c) in view of driving stability. In this embodiment, the coolant inlet 72b is disposed as described above, and the portion of the exhaust unit coolant flow path 72 located near the exhaust port 55 at the lower portion of the other end wall portion 10c is first cooled by the coolant having a lower temperature, and the coolant thus cooled against the other end wall portion 10c is discharged upward so as to pass through the exhaust unit coolant outlet connection portion 72 d. At this time, the coolant is heat-exchanged to increase its temperature, thereby reducing its specific gravity and generating a vector of upward flow. This flow of the coolant can effectively cool the portion of the lower exhaust port 55, and can match the directionality of the flow caused by the temperature rise of the coolant with the directionality of the flow for discharging the coolant upward. Therefore, the coolant can smoothly pass through the cooling device, and the cooling efficiency can be effectively improved.

Further, according to the present embodiment, the exhaust unit coolant flow path 72 is provided by disposing the first flow path forming portion 61 on the other end wall portion 10c of the pump chamber body portion 110, and the first flow path forming portion 61 includes the coolant flow path forming surface 61a, and the exhaust unit coolant flow path 72 is formed between the coolant flow path forming surface 61a and the outer surface of the other end wall portion 10c, the coolant flow path forming surface being disposed so as to cover the outer surface side of the other end wall portion 10c. This enables the exhaust unit coolant flow field 72 to be configured efficiently and rationally.

As shown in fig. 13, 20, and 21, the first flow path forming section 61 of the present embodiment is provided by a plate-like member having irregularities formed on both surfaces thereof so as to form flow paths, is fixed to the outer surface of the other end wall section 10c by bolts, and is watertight sealed at the joint by a seal member 65 to form the exhaust section coolant flow path 72. The joint portion of this 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 an annular frame shape to abut against the peripheral edge portion of the other end wall portion 10c. Thus, the following configuration is obtained: an exhaust portion coolant flow path 72 is formed between the inner ring joint portion 61c and the outer ring joint portion 61d, and is filled with coolant. Thus, the following forms are obtained: the outer wall surface of the other end wall portion 10c can be efficiently cooled by bringing the entire surface of the coolant into contact with the wall surface. In addition, this structure is compact in structure in which the layered discharge section coolant flow paths 72 are stacked in a planar manner outside the outer end surfaces of the pump chamber main body sections 110.

In addition, the first channel forming unit 61 of this embodiment is provided in the following manner: on the coolant flow path forming surface 61a which is a surface (opposite surface) facing the outer surface of the other end wall portion 10c, a passage forming wall constituting the coolant flow restriction portion 61b is projected so as to form an exhaust port peripheral flow path portion 72c which is a groove-shaped passage and which is a part of the exhaust portion coolant flow path 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 restricting portion 61 b) for appropriately bending and guiding the exhaust unit coolant flow field 72 is provided on the coolant flow field forming surface 61a side of the first flow field 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.

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

According to the exhaust flow path 56, the overheated exhaust gas can be efficiently cooled, the temperature of the exhaust gas can be reduced, the temperature in the pump chamber 10 can be reduced, and the thermal expansion due to overheating of the constituent members forming the pump chamber 10, such as the pump chamber body 110 and the two rotors 30A and 30B, can be uniformly suppressed.

The exhaust flow path 56 can appropriately restrict the flow direction of the exhaust gas, and is in a form of promoting cooling of the exhaust gas, and also serves as a structure of a muffler for reducing exhaust sound. That is, the first muffler portion 31 is configured by a structure in which the exhaust gas flow passage 56 is formed. Further, reference numeral 57 denotes an exhaust port of the first muffler portion, which is provided so as to open to the upper wall portion of the first flow path forming portion 61, and serves as an exhaust port of the exhaust flow path 56, and which exhausts the gas 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 portion of this embodiment is formed in a shape in which the flow path is narrowed on the inner side, and is formed so that the muffling effect can be improved.

Further, according to this embodiment, the exhaust gas flow path 56 is provided by disposing the second flow path forming portion 62 in the first flow path forming portion 61, and the second flow path forming portion 62 includes the exhaust gas flow path forming surface 62a, and the exhaust gas flow path forming surface 62a is a portion disposed so as to cover the outer surface side of the first flow path forming portion 61 and is provided so as to form the exhaust gas flow path 56 between the outer surface of the first flow path forming portion 61 and the exhaust gas flow path forming surface 62 a. This enables the exhaust flow path 56 to be configured efficiently and rationally, and the exhaust gas just after the exhaust port to be cooled efficiently on both the exhaust flow path forming surface 61e and the exhaust flow path forming surface 62 a. In addition, this structure is compact in structure because the layered exhaust gas flow passages 56 are planarly stacked outside the outer end surface of the pump chamber body 110.

As shown in fig. 13 and the like, the second flow path forming portion 62 of the present embodiment is provided by a plate-like member in which an exhaust gas flow path forming surface 62a as an inner surface (a surface abutting on the outer surface side of the first flow path forming portion 61) is formed flatly, and is fixed to the outer surface (the exhaust gas flow path forming surface 61 e) side of the first flow path forming portion 61 by a bolt. Further, an exhaust passage forming wall 61f is provided on the outer surface (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) so as to form a groove-like passage serving as the exhaust passage 56. The annular frame-shaped joining portion 61g or the exhaust passage forming wall 61f, which is the outer peripheral portion on the outer surface side of the first flow passage forming portion 61, and the inner surface of the second flow passage forming portion 62 can be brought into a substantially airtight state by being fixed in close contact therewith, or an airtight state can be formed by providing a sealing member. 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. Further, as shown in fig. 21, the exhaust gas flow passage 56 is formed as a complicated curved flow passage, whereby cooling of the exhaust gas can be further promoted, and exhaust sound can be further reduced by appropriately functioning as a muffler chamber.

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 includes the 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 with the outer surface (extension flow path forming surface 62 b) of the second flow path forming portion 62. This enables extension-side coolant flow field 73 to be configured efficiently and rationally. This structure is configured such that the extension coolant flow passages 73 having a layered shape are stacked in a planar manner outside the outer end surface of the pump chamber body 110, and is compact. Further, noise can be reduced by the extension portion cooling liquid passage 73 having a layer shape and the structural wall constituting the extension portion cooling liquid passage 73. That is, the extension portion coolant flow path 73 and the exhaust portion coolant flow path 72 are formed to shield sound and reduce noise, and are also components of the first muffler portion 31.

Further, as shown in fig. 13 and the like, the third flow passage forming portion 63 of the present embodiment is provided by a flat plate-like member (plate-like member), is provided so as to be fixed to the outer surface side of the second flow passage forming portion 62 by a bolt, and is water-tightly sealed by a seal member 65 to a peripheral edge joining portion 62c provided in an annular frame shape on the outer surface of the second flow passage forming portion 62, thereby forming an extended portion coolant flow passage 73. In the present embodiment, the extension coolant flow path 73 is in a form in which the coolant is retained in a space formed in a flat layer shape, but the present invention is not limited to this, and the flow path may be set to an appropriate form. Further, the extension coolant flow field 73 may be formed in multiple layers to improve the cooling performance. In addition, in the extension portion coolant flow path 73, an extension portion coolant outlet connection portion 73b is provided at an upper portion so as to be connected to the exhaust portion coolant flow path 72 via the second connection pipe 72e from an exhaust portion coolant outlet connection portion 72d provided at an upper portion of the second connection pipe 72e and connected to the exhaust portion coolant flow path 72, and to be connected to an extension portion coolant inlet connection portion 73a provided at a lower portion of the second connection pipe 72e, and to discharge the coolant flowing through the extension portion coolant flow path 73 to the outside, and the coolant flows so as to generate a flow from the lower portion to the upper portion in the same manner as the exhaust portion coolant flow path 72.

In this embodiment, 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, 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 by a member divided into two, but the present invention is not limited to this, and may be formed by a member mainly divided into three, for example, the cylinder portion 10a, one end wall portion 10b, and the other end wall portion 10c.

Next, a configuration example of a structure of the bearing portion 40 that axially supports the two rotary shafts 20A and 20B in cooling the two-shaft rotary pump of the present invention will be described in detail with reference to the drawings (fig. 13 to 21). As described above, the twin-shaft rotary pump of the present embodiment is a canned rotary pump unit, but the present invention is not limited thereto, and can be applied to other twin-shaft rotary pumps such as roots pumps and screw pumps. The present invention is not limited to the form in which the two rotors 30A and 30B are supported and supported by the shafts in a cantilever state as in the present embodiment, and the present invention can also be applied to a form in which the rotary shafts 20A and 20B are supported and supported by the shafts in a rotatable manner at both ends.

As shown in fig. 13, the two-shaft rotary pump of the present invention includes a bearing body 120, the bearing body 120 constituting a structural wall portion 121, the structural wall portion 121 being provided with a bearing portion 40 that pivotally supports two rotary shafts 20A, 20B, and serving as a gear case 45, the gear case 45 incorporating a pair of gears 21A, 21B that are provided corresponding to the two rotary shafts 20A, 20B and mesh with each other. The bearing body 120 of this embodiment is provided with a bearing portion 40 that pivotally supports 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 are supported in a cantilever state. The bearing body 120 and the pump chamber body 110 constitute a pump body 100 of the double-shaft rotary pump.

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

This has a particularly advantageous effect of being able to extend the life of the functional components constituting the bearing 40 and the like by reducing the heat transfer prevention effect of the heat transfer of the compressed gas (exhaust gas) generated by the driving of the two rotors 30A, 30B to the bearing main body portion 120 and the cooling effect of the coolant passing through the bearing portion coolant flow path 71. 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, the heat transfer can be suppressed to minimize the amount of heat transfer, and the bearing main body 120 can be cooled more actively 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 rise of the lubricating oil could be reduced by about 40 ℃.

Further, the functional components are constituent components including the bearing 41 and the oil seal 42, and are handled as consumable components. By extending the life of these functional components, the running cost can be reduced.

The bearing portion 40 of the present embodiment is configured by a first bearing portion 40A and a second bearing portion 40B, the first bearing portion 40A is provided on a structural wall portion (one structural wall portion 121A) on the pump chamber main body portion 110 side of the bearing main body portion 120 so as to support the two rotary shafts 20A and 20B between the two gears 21A and 21B and the two rotors 30A and 30B, and the second bearing portion 40B is provided on a structural wall portion (the other structural wall portion 121B) opposite to the first bearing portion 40A and disposed on the side to which the drive motor (the electric motor 3 (see fig. 3 and the like)) is coupled so as to support the two rotary shafts 20A and 20B. The rotary shaft 3a of the electric motor 3 is coupled to a coupling 3b (see fig. 4 and the like) via a rotary shaft 20A (drive-side rotary shaft).

In this embodiment, the two rotary shafts 20A and 20B are horizontally disposed to be horizontal, and the bearing portion cooling liquid flow path 71 is provided below the structural wall portion 121 of the bearing body 120 so as to pass below the liquid surface of the lubricating oil in the stored state at rest, thereby cooling the lubricating oil stored in the gear case 45. The liquid level of the lubricating oil at rest is set to be located between the inner bottom surface of the gear case 45 (oil chamber) and the rotating shafts 20A and 20B arranged horizontally. This allows the lubricating oil to be efficiently cooled, and the lubricating oil is lifted by the two rotating gears 21A and 21B, thereby lubricating the gears 21A and 21B and the bearing 41 and cooling the gear case 45.

In addition, the present embodiment is as follows: the bearing portion cooling liquid flow path 71 is provided in the shape of a straight through hole in a lower portion of the first bearing portion 40a (a lower side of the bearing 41 of the first bearing portion 40 a) of the bearing body portion 120, and is partially disposed. This has the following effects: the portions of the bearing body 120 that are likely to conduct heat from the pump chamber body 110 side are actively cooled, and the lubricating oil can be efficiently cooled.

Further, in this embodiment, the discharge port 55 of the pump chamber 10 is provided at the lower portion of the pump chamber main body portion 110. As a result, when the bearing portion cooling liquid flow path 71 is provided below the structural wall portion 121 of the bearing body 120 as described above, heat conduction is effectively suppressed, and overheating of the bearing portion 40 can be suppressed.

Further, in addition to the horizontal type in which the two rotary shafts 20A and 20B are horizontally arranged as in this embodiment, an air blowing means for flowing air so as to escape from the lower side toward the upper side may be provided in the cooling gap 60. This enables the pump chamber body 110 and the bearing body 120 to be efficiently cooled down, and the reliability of the biaxial rotation pump can be further improved. That is, since the cooling air can be appropriately flowed between the pump chamber body 110 and the bearing body 120, heat transfer can be more effectively suppressed, and cooling by heat radiation can be promoted. This can suppress a temperature rise in the bearing main body 120, and can prolong the life of the functional components.

Further, according to the double-shaft rotary pump of the present invention, the bearing portion cooling liquid flow path 71 is connected to the cooling liquid flow path provided in the pump chamber body portion 110, so that the cooling liquid that cools the bearing body portion 120 cools the pump chamber body portion 110. As a result, the temperature of the coolant flowing through the bearing section coolant flow path 71 can be made lower than the temperature of the coolant flowing through the coolant flow path provided in the pump chamber body 110 so as not to overheat the lubricant by boiling, and the coolant can be effectively used.

In this embodiment, the bearing portion cooling liquid flow path 71 is connected to the exhaust portion cooling liquid flow path 72 so that the cooling liquid flows in the order from the bearing portion cooling liquid flow path 71 to the exhaust portion cooling liquid flow path 72. Thus, the structural wall portion 121 (one structural wall portion 121 a) of the bearing portion 40 (first bearing portion 40 a) of the bearing body 120 and the other end wall portion 10c of the pump chamber body 110 can be directly and efficiently cooled in sequence 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 portion 71a (fig. 15, 17, and 19), the bearing portion coolant flow field 71 (fig. 13 and 19), and the bearing portion coolant outlet connection portion 71b (fig. 14, 16, 18, and 19) in this order, then flows through the first connection pipe 71c (fig. 14, 16, 18, and 19), the exhaust portion coolant inlet connection portion 72a (fig. 14, 16, and 18), and the coolant introduction port 72b (fig. 20) in this order, is supplied to the exhaust portion coolant flow field 72 (fig. 13 and 20), and is discharged to the outside of the pump 2 through the extension portion coolant flow field 73. It is needless to say that the bearing portion cooling liquid flow path 71 and the exhaust portion cooling liquid flow path 72 are not connected, and the cooling liquid may be supplied separately, or the supply of the cooling liquid may be adjusted independently, whereby optimization can be performed.

In the flow path 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 according to this embodiment, 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, and the directionality of the flow caused by the temperature rise of the cooling liquid and the directionality of the flow of the cooling liquid are aligned, whereby the cooling liquid can smoothly flow, and the bearing portion 40 and the exhaust gas can be efficiently cooled.

According to the cooling structure of the double-shaft rotary pump described above, the cooling performance can be improved appropriately for the canned rotary pump unit, and the pump performance can be improved. In the packaged rotary pump unit of the present invention, as described above, the structure in which the lower side of the pump chamber 10 is easily overheated and can be cooled from the lower side thereof is appropriately formed. Therefore, the pump chamber 10 can be efficiently cooled, the pump performance can be improved, and the particularly advantageous effect of enabling the life of the functional components to be lengthened can be achieved as described above.

In this embodiment, as shown in fig. 13 to 19, the cooling gap 60 between the pump chamber body 110 and the bearing body 120 is formed in such a manner that one end wall portion 10b and one structural wall portion 121a provided with the first bearing portion 40a facing the one end wall portion 10b are integrated by the plurality of columnar portions 115, and the cooling gap 60 is formed in a portion where the columnar portion 115 is not provided. Such a shape may be formed by, for example, forming the cooling gap 60 with a core in the case of manufacturing by casting. The present invention is not limited to this, and it goes without saying that the cooling gap 60 can be formed by connecting the member on the pump chamber body 110 side including the one end wall portion 10b and the member on the bearing body 120 side constituting the structural wall portion 121 of the bearing portion 40 facing the one end wall portion 10b, which are formed by different members, by the columnar connecting portions 111 and 122 formed on both sides, as shown in fig. 22.

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

This prevents reverse flow of exhaust gas, suppresses overheating of the pump chamber 10, and improves pump performance. This effect of preventing backflow of exhaust gas and the above-described synergistic effect such as the cooling effect of the coolant can more effectively prevent overheating of the pump chamber 10, and improve the pump performance.

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

In the present invention, for example, the temperature of the coolant can be controlled to cope with the use in cold regions, and the range of use of the present invention can be expanded, and the coolant can be cooled by using a heat exchanger in a coolant circulation system.

While the present invention has been described in various embodiments, it is to be understood that the present invention is not limited to the embodiments, and various changes and modifications may be made without departing from the spirit of the present invention.

Description of the symbols

1-a closed casing, 1A-a casing frame portion, 1B-a base portion, 1 c-a casing cover portion, 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, 5 a-a pipe for heat exchange, 5B-a coolant connection pipe, 6-an air blowing device, 7-an air blowing fan, 8-a distribution board, 9-a blower for cooling an electrical component, 10-a pump chamber, 10A-a cylinder portion, 10B-one end wall portion, 10 c-the other end wall portion, 11-a cylinder housing, 12-a side plate, 14-an air suction port, 15-an air suction port, 16-an air suction introduction pipe connection port, 17-a check valve, 20A-a rotary shaft (drive-side rotary shaft), 20B-a rotary shaft (driven-side rotary shaft), 21A-a gear (drive-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 (drive-side rotor), 30B-a rotor (driven-side rotor), 31-a first muffler portion, 32-a second muffler portion, 33-a vibration damping piping, 34-an exhaust gas inlet port of the second muffler portion, 35-an exhaust gas outlet port of the second muffler portion, 37-a hanger 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 preceding stage air vent, 55-an exhaust port, 56-an exhaust gas flow path, 57-an exhaust port of the first muffler portion, <xnotran> 60 — ,61 — ,61a — ,61b — ,61c — ,61d — ,61e — ,61f — ,61g — ,62 — ,62a — ,62b — ,62c — ,63 — ,63a — ,65 — ,71 — ,71a — ,71b — ,71c — ,72 — ,72a — ,72b — ,72c — ,72d — ,72e — ,73 — ,73a — ,73b — ,81 — ,82 — ,83 — ,90 — ,91 — ,92 — ,93 — ,94 — ,100 — ,110 — ,115 — ,120 — ,121 — ,121a — ,121b — ,200 — ,300 — . </xnotran>

Claims (17)

1. A packaged rotary pump unit is provided with: an electric rotary pump including a rotary pump for sucking and discharging gas and an electric motor for driving the rotary pump; and a sealed casing in which the electric rotary pump is built, the sealed rotary pump unit being characterized by comprising:

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

a blower device which is disposed inside the sealed casing and which cools the inside air in the sealed casing by sending the inside air including heated air to the liquid-cooled heat exchanger, wherein the heated air is generated by heating air around the rotary pump by operation of the rotary pump,

the rotary pump is a two-shaft rotary pump, one rotor rotating shaft is connected in series to the rotating shaft of the electric motor to rotate, the other rotor rotating shaft is synchronously rotated in a direction opposite to the one rotor rotating shaft via a gear, and the liquid cooling heat exchanger and the air blowing device are disposed in a space on an extension line of an axis of the other rotor rotating shaft, that is, a space adjacent to a portion where the electric motor and the one rotor rotating shaft are connected.

2. The encapsulated rotary pump unit of claim 1,

the rotary pump device is provided with a pump cover part which is arranged in the closed box body and covers the rotary pump, and is formed by being provided with: a circulating air inlet part for introducing the internal air circulating in the closed box; and a circulating air outlet part discharging the internal air including the heated air.

3. The encapsulated rotary pump unit of claim 2,

the liquid cooling heat exchanger is connected to the side of the circulating air outlet portion,

the air blowing 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 encapsulated rotary pump unit of claim 1,

the electric motor is provided with an electric motor cooling air supply fan for supplying air to cool the electric motor, and the air supply fan is arranged on the side opposite to the side connected to the one rotor rotating shaft and supplies air to the motor main body.

5. The encapsulated rotary pump unit of claim 1,

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

6. The encapsulated rotary pump unit of claim 1,

comprises a pump cover part and a pump cover part,

the pump cover portion is disposed inside the sealed casing, is provided so as to cover a periphery of the rotary pump except the electric motor in the electric rotary pump, and is formed so as to include: a circulating air inlet part for introducing the internal air circulating in the closed box; and a circulating air outlet part discharging the internal air including the heated air,

the circulating air inlet portion is provided in a band-like open shape so as to surround the periphery of the rotary pump.

7. The encapsulated rotary pump unit of claim 6,

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

the pump cover portion is provided so as to cover the peripheries of the bearing main body portion and the pump chamber main body portion.

8. The encapsulated rotary pump unit of claim 7,

the liquid cooling heat exchanger is connected to the side of the circulating air outlet portion,

the air supply device is connected to the liquid-cooled heat exchanger to draw the internal air, so that the internal air flows from the circulating air inlet part to the circulating air outlet part and passes through the liquid-cooled heat exchanger.

9. A packaged rotary pump unit is provided with: an electric rotary pump including a rotary pump for sucking and discharging gas and an electric motor for driving the rotary pump; and a sealed box body in which the electric rotary pump is built, the sealed rotary pump unit being characterized by comprising:

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

a blower device which is disposed inside the sealed casing and which cools the inside air in the sealed casing by sending the inside air including heated air to the liquid-cooled heat exchanger, wherein the heated air is generated by heating air around the rotary pump by operation of the rotary pump,

a liquid cooling flow path from the liquid cooling heat exchanger is connected in series across the liquid cooling heat exchanger and the rotary pump so that the rotary pump is also cooled by the liquid cooling heat exchanger and the liquid cooling fluid from the liquid cooling supply.

10. The encapsulated rotary pump unit of claim 9,

the rotary pump comprises a bearing main body part, a pump chamber main body part, and a first silencer part,

the liquid cooling passages from the coolant supply source are connected in series so that the coolant from the coolant 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.

11. The encapsulated rotary pump unit of claim 9,

the rotary pump device is provided with a pump cover part which is arranged in the closed box body to cover the rotary pump, and is formed by being provided with: a circulating air inlet part for introducing the internal air circulating in the closed box; and a circulating air outlet part discharging the internal air including the heated air.

12. The encapsulated rotary pump unit of claim 11,

the liquid cooling heat exchanger is connected to the side of the circulating air outlet portion,

the air blowing 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.

13. The encapsulated rotary pump unit of claim 9,

the rotary pump is a two-shaft rotary pump, and is configured such that one rotor rotating shaft is connected in series to the rotating shaft of the electric motor and rotates, and the other rotor rotating shaft synchronously rotates in a direction opposite to the one rotor rotating shaft via a gear,

the liquid-cooled heat exchanger and the air blowing device are disposed in a space on an extension line of the axis of the other rotor rotating shaft, that is, a space adjacent to a portion where the electric motor and the one rotor rotating shaft are connected.

14. The encapsulated rotary pump unit of claim 13,

the electric motor is provided with an air supply fan for cooling the electric motor for supplying air to cool the electric motor,

the blower fan is disposed on the side opposite to the side connected to the one rotor rotation shaft, and blows air to the motor main body.

15. The encapsulated rotary pump unit of claim 9,

comprises a pump cover part and a pump cover part,

the pump cover portion is disposed inside the sealed casing, is provided so as to cover a periphery of the rotary pump except the electric motor in the electric rotary pump, and is formed so as to include: a circulating air inlet part for introducing the internal air circulating in the closed box; and a circulating air outlet part discharging the internal air including the heated air,

the circulating air inlet portion is provided in a band-like open shape so as to surround the periphery of the rotary pump.

16. The encapsulated rotary pump unit of claim 15,

the rotary pump comprises a bearing main body part, a pump chamber main body part and a first silencer part,

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

17. The encapsulated rotary pump unit of claim 16,

the liquid cooling heat exchanger is connected to the side of the circulating air outlet portion,

the air supply device is connected to the liquid cooling 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 cooling heat exchanger.

Images