JP7057609B1 - Package type rotary pump unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To maintain high pump performance by preventing the internal air of a closed housing from being overheated even when the rotary pump contained in the closed housing is used as a vacuum pump in a range having a high degree of vacuum. It is possible to provide a package type rotary pump unit that can prolong the life of the equipment. SOLUTION: This is a package type rotary pump unit including an electric rotary pump 200 and a closed housing 1 including the electric rotary pump 200, which is arranged inside the closed housing 1 and outside the closed housing 1. The liquid-cooled heat exchanger 5 that is cooled by receiving the supply of the coolant from the coolant supply source 4 arranged in the air-sealed housing 1 and the surroundings of the rotary pump 2 by the operation of the rotary pump 2 are arranged inside the sealed housing 1. A blower 6 that sends the internal air in the sealed housing 1 including heated air generated by heating the air to the liquid-cooled heat exchanger 5 so as to cool it, and a liquid-cooled flow path from the coolant supply source. Is connected in series to the liquid-cooled heat exchanger and the rotary pump. [Selection diagram] Fig. 1

Description

The present invention relates to a package type rotary pump unit including a rotary pump for sucking and exhausting gas, an electric rotary pump including an electric motor for driving the rotary pump, and a closed housing including the electric rotary pump.

As a conventional package type rotary pump unit, there are an air pressure device such as a vacuum pump and a blower that generates negative pressure and positive pressure air pressure, and a storage box that can store a plurality of the air pressure devices and can be soundproofed by storing them in a closed space. In order to take in outside air and cool the inside of the storage box heated by the pneumatic device, a blower device for generating and exhausting a cooling air flow substantially flowing from below to above in the storage box, and the above-mentioned A water-cooled cooler provided to pass a cooling air flow to cool, a cooler unit that supplies cold water to the cooler, and a water temperature that controls the temperature of the cold water supplied to the cooler. At least one of a water temperature controlling means for controlling the water temperature and a flow rate controlling means for controlling the flow rate so as to adjust the flow rate of the cold water supplied to the cooler is provided, and the air pressure is provided in the middle portion in the height direction in the storage box. The exhaust temperature adjustment of the pneumatic device station is characterized in that a shelf-shaped support portion on which the device is placed is provided at least one stage, and the shelf-shaped support portion has an opening portion so as to allow the flow of the cooling air flow. A system (see Patent Document 1) has been proposed by the applicant.

Further, as an example of the rotary pump built in the package type rotary pump unit, as shown in FIG. 22, the applicant forms a pump chamber 10 having a cross-sectional shape in which a part of two circles is overlapped. The pump chamber is provided with 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. Two rotating shafts 20A and 20B arranged in parallel in 10 and rotated at the same speed in opposite directions and two rotating shafts 20A and 20B provided in each of the two rotating shafts 20A and 20B are arranged in the pump chamber 10 and mutually. Two rotors 30A and 30B having a hook-shaped claw portion formed so that the inhaled gas can be compressed and exhausted by being rotated in a non-contact state, and the one end wall portion 10b and the other end wall portion. A rotary pump (claw pump) having an exhaust side opening 50 provided at least one of the 10c at a position facing the portion where the gas is compressed in the pump chamber 10. The exhaust side opening 50 is connected to the front vent 51 which is communicated to the outside of the pump chamber 10 before the gas compression ratio is maximized by the claws of the two rotors 30A and 30B. , A rear stage exhaust port (exhaust port) that is communicated so as to be exhausted to the outside of the pump chamber 10 including a step in which the compression ratio of the gas is maximized by the claws of the two rotors 30A and 30B as compared with the previous stage. The front-stage vent 51 is closed by the rotor 30A at the stage where the rear-stage exhaust port (exhaust port 55) is communicated with the outside of the pump chamber 10 to maximize the compression ratio of the gas. The pump chamber body portion provided by the end wall portions 10b and 10c provided on each of the cylinder portion 10a and both end faces of the cylinder portion so as to form the pump chamber 10, and the two rotors. A bearing body provided with a bearing portion 40 for bearing the two rotating shafts 20A and 20B so that 30A and 30B are arranged at one end of the two rotating shafts 20A and 20B and are supported in a cantilevered state, respectively. A claw pump has been proposed in which the pump body is provided in a divided structure so that a cooling gap is formed between the pump and the pump (see Patent Document 2).

According to the claw pump proposed by the present applicant, the exhaust side opening 50 is composed of a front-stage ventilation port 51 and a rear-stage exhaust port (exhaust port 55) provided separately. Therefore, for example, when the pump is used as a vacuum pump with a high degree of vacuum, the outside air that has not been overheated in the front ventilation port 51 is sucked into the pump chamber 10, so that the exhaust flows back in the rear exhaust port (exhaust port 55). This can be suppressed and the pump chamber 10 can be prevented from being overheated, so that the pump performance can be improved.

Japanese Patent No. 5041849 (Claim 1, FIG. 1) Japanese Patent No. 6479714 (Claim 1, FIG. 3)

The problem to be solved with respect to the package type rotary pump unit has been proposed in the conventional package type rotary pump unit in which cooling air is introduced from the outside and the air heated by the rotary pump is discharged to the outside of the housing. However, when the rotary pump is built in the closed housing and the air heated by the rotary pump is not discharged to the outside of the closed housing, the inside of the closed housing is effectively prevented from being overheated. The means have not been considered. That is, if the inside of the sealed housing is overheated by the operation of the rotary pump and the temperature of the internal air rises, it adversely affects the electric motor, electrical components, and the like, so appropriate temperature measures are required.

Therefore, an object of the present invention is that the internal air of the closed housing is overheated even when the rotary pump contained in the closed housing is used as a vacuum pump in a high vacuum range and the amount of heat generated is large. It is an object of the present invention to provide a package type rotary pump unit which can maintain high pump performance and prolong the life of the device by being able to prevent it.

The present invention comprises the following configurations in order to achieve the above object.
According to one form of the package type rotary pump unit according to the present invention, an electric rotary pump including a rotary pump for sucking and exhausting gas and an electric motor for driving the rotary pump, and a sealed housing containing the electric rotary pump. A liquid-cooled heat exchanger that is a package-type rotary pump unit provided with a And, the internal air in the closed housing, which is arranged inside the closed housing and contains the heated air generated by heating the air around the rotary pump by the operation of the rotary pump, is transferred to the liquid-cooled heat exchanger. A liquid-cooled flow from the coolant supply source is provided so that the rotary pump is also cooled by the coolant from the coolant supply source that has cooled the liquid-cooled heat exchanger. The path is connected in series to the liquid-cooled heat exchanger and the rotary pump.

Further, according to one form of the package type rotary pump unit according to the present invention, the rotary pump includes a bearing body portion, a pump chamber body portion, and a first muffler portion, and the coolant from the coolant supply source is provided. However, the liquid-cooled flow path from the coolant supply source is connected in series so that the liquid-cooled heat exchanger, the bearing body portion, the pump chamber body portion, and the first muffler portion flow in this order. Can be.

Further, according to one form of the package type rotary pump unit according to the present invention, the internal air that is arranged inside the closed housing and is provided so as to cover the rotary pump and circulates inside the closed housing. It can be characterized by including a pump cover portion formed so as to be provided with a circulating air inlet portion into which the air is introduced and a circulating air outlet portion from which the internal air including the heated air is discharged.

Further, according to one form of the package type rotary pump unit according to the present invention, the liquid-cooled heat exchanger is connected to the side of the circulating air outlet portion, and the blower sucks the internal air to circulate the air. It can be characterized in that it is connected to the liquid-cooled heat exchanger so as to flow from the air inlet portion to the circulating air outlet portion and pass through the liquid-cooled heat exchanger.

Further, according to one form of the package type rotary pump unit according to the present invention, the rotary pump is a biaxial rotary pump, and one rotor rotary shaft is connected in series with the rotary shaft of the electric motor and is rotated. , The other rotor rotation shaft is provided so as to be rotated in synchronization with the direction opposite to the one rotor rotation shaft via a gear, and the space on the extension of the axis on which the other rotor rotation shaft is arranged. The liquid-cooled heat exchanger and the blower device may be arranged in a space adjacent to a portion where the electric motor and the one rotor rotation shaft are connected.

Further, according to one form of the package type rotary pump unit according to the present invention, the electric motor is provided with a blower fan for cooling the electric motor that blows air so as to cool the electric motor, and the blower fan is the above-mentioned blower fan. It can be characterized in that it is arranged on the side opposite to the side connected to one rotor rotating shaft and is provided so as to blow air toward the motor main body.

According to the package type rotary pump unit according to the present invention, when the rotary pump unit is operated in a high temperature environment, or when the rotary pump contained in a closed housing is used as a vacuum pump, for example, in a high vacuum range and has a large calorific value. However, by preventing the internal air of the sealed housing from being overheated, high pump performance can be maintained and the life of the device can be extended, which is a special advantageous effect.

It is a block diagram which shows typically the liquid cooling flow of the form example of the package type rotary pump unit which concerns on this invention, and the circulating gas (air) flow inside a closed housing. It is a block diagram which shows typically the liquid cooling flow and the exhaust flow of the form example of the package type rotary pump unit which concerns on this invention. It is an example of the form of the package type rotary pump unit which concerns on this invention, and is the perspective view which shows the inside of the closed housing. It is a perspective view which shows the state which removed the pump cover part of the form example of FIG. It is a top view of the electric rotary pump mounted on the form example of FIG. It is a top view which shows the state which removed the pump cover part of the form example of FIG. It is a rear view of the morphological example of FIG. It is a perspective view which shows the appearance of the form example in which two electric rotary pumps of the package type rotary pump unit which concerns on this invention are housed in two upper and lower stages. It is a perspective view which shows the internal structure of the closed housing of the form example of FIG. It is a side view which shows the internal structure of the closed housing of the form example of FIG. FIG. 8 is a perspective view showing an internal structure of a closed housing of the embodiment of FIG. 8 with the switchboard removed. FIG. 8 is a front view showing the internal structure of the sealed housing of the embodiment of FIG. 8 with the switchboard removed. It is sectional perspective view which showed the state which was broken in the step shape as shown the internal structure of the form example of the rotary pump (claw pump) mounted on the package type rotary pump unit which concerns on this invention. It is a front side perspective view of the form example of FIG. It is a back side perspective view of the form example of FIG. It is a front view of the morphological example of FIG. It is a back view of the form example of FIG. It is a top view of the morphological example of FIG. It is sectional drawing which shows the bearing part coolant flow path of the form example of FIG. FIG. 3 is an exploded view showing a coolant flow path forming surface which is an inner surface of the first flow path forming portion in the embodiment of FIG. 13. It is an exploded view which shows the exhaust flow path formation surface which is the outer surface of the 1st flow path formation part in the form example of FIG. It is an exploded view which shows the conventional rotary pump.

Hereinafter, an example of the form of the package type rotary pump unit according to the present invention, in which a claw pump is mounted as an example of the rotary pump, will be described in detail with reference to the accompanying drawings (FIGS. 1 to 21). An example of the form of the rotary pump according to the present invention is a vacuum pump, which is a water-cooled biaxial rotary pump (claw pump). However, the rotary pump according to the present invention is not limited to this embodiment, and includes a pump that can be used as a blower or the like whose discharged gas is a product gas, or a uniaxial rotary pump such as a vane pump, and is water. Includes those that use other than as a coolant.

As a basic configuration, the package type rotary pump unit according to the present invention includes an electric rotary pump 200 including a rotary pump 2 for sucking and exhausting gas and an electric motor 3 for driving the rotary pump 2, and the electric rotary pump 200 thereof. It is provided with a closed housing 1.

The sealed housing 1 according to the present invention does not need to be strictly airtightly sealed, and the inflow and outflow of gas (air in this embodiment) between the inside of the housing and the outside world is sufficient. Any housing that forms a closed space limited to is sufficient, and has a degree of airtightness that is substantially free from the influence of outside air (outside air) on the circulation of the internal air in the closed housing 1. Just do it. That is, in the closed housing 1 according to the present invention, a slight gap is allowed, and structural members such as steel plates constituting the housing are brought into contact with each other without using a sealing material as in the example of the present invention. The degree of sealing may be such that the flow of air is sufficiently restricted.

Further, the sealed housing 1 of this embodiment has a rectangular box shape, and has a housing frame portion 1a (see FIGS. 3 and 9), a base portion 1b (see FIGS. 3 and 9), and a housing cover. A unit 1c (see FIG. 8) is provided. The sealed housing 1 is configured such that the housing frame portion 1a formed of a square steel pipe, angle steel, or the like as a skeleton structure is covered with a housing cover portion 1c formed of a steel plate or the like.
Inside the sealed housing 1, an electric rotary pump 200 including a rotary pump 2 and an electric motor 3, a liquid-cooled heat exchanger 5, a blower device 6, a pump cover section 25, a power distribution board 8, a first muffler section 31, a first The muffler portion 32 of No. 2, the blower 9 for cooling the electrical components, the drain pan 91, various pipes, various electric wirings, and their accessories are arranged.

Reference numeral 5 is a liquid-cooled heat exchanger, and as shown in FIGS. 1 and 3 to 7, the cooling liquid is supplied from the cooling liquid supply source 4 arranged inside the closed housing 1 and outside the closed housing 1. It is provided to be supplied and cooled. 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 4b. In FIG. 1, the flow of the coolant is schematically shown by double-lined arrows.

The liquid-cooled heat exchanger 5 of this embodiment is a so-called fin and tube in which a heat exchange conduit 5a through which a cooling liquid passes is housed in a rectangular box-shaped heat exchange chamber in a reciprocating state (zigzag). It is provided in the form of. Then, in the rectangular box-shaped heat exchange chamber of the present embodiment, the rectangular introduction port on the side where the internal air (circulating air) is introduced is connected to the circulating air outlet portion 25b of the pump cover portion 25 described later. A rectangular discharge port on the side where the internal air (circulating air) is discharged is connected to a blower device 6 described later. This constitutes a fan cooler having a liquid-cooled heat exchanger 5. The liquid-cooled heat exchanger 5 is not shown in detail because it is a general aspect. Of course, as the liquid-cooled heat exchanger 5, the form of the flow path of the cooling liquid and the form of the passage of the circulating air cooled by the heat exchange can be appropriately and selectively set.

Here, as the coolant supply source 4, a liquid cooling device that cools the liquid by using a refrigeration cycle can be used. Depending on the location conditions, other cooling sources such as air (outside air), fresh water, seawater, ice, and groundwater may be used, and of course, a plurality of cooling sources may be appropriately combined and used. Is. The coolant of this embodiment is cooling water, and as will be described later, it is supplied from the same coolant supply source 4 that cools the exhaust discharged from the exhaust port 55.

Reference numeral 6 is a blower, which is arranged inside the closed housing 1, and is contained in the closed housing 1 containing heated air generated by heating the air around the rotary pump 2 by the operation of the rotary pump 2. It is provided as a means for sending the internal air to the liquid-cooled heat exchanger 5 so as to be cooled. In FIG. 1, the flow of the internal air is schematically shown by a thick arrow.
The blower 6 of this embodiment is an axial flow fan, and is arranged so as to suck and discharge the internal air along the longitudinal direction of the electric rotary pump 200. The blower 6 is not limited to the axial fan, and of course, another blower means such as a centrifugal fan (for example, a sirocco fan) may be selectively used.

According to the package type rotary pump unit according to the present invention, when the rotary pump unit is operated in a high temperature environment, or when the rotary pump 2 contained in the sealed housing 1 is used as a vacuum pump, for example, in a high vacuum degree range, the amount of heat generated is generated. Even when the size is large, it is possible to prevent the internal air of the sealed housing 1 from being overheated, so that high pump performance can be maintained and the life of the apparatus can be extended, which is a special advantageous effect. That is, by flowing the internal air in the sealed housing 1 by the blower 6 and passing it through the liquid-cooled heat exchanger 5, it is possible to prevent the superheated air from stagnation around the rotary pump 2 and to make the internal air efficient. Can be circulated well and cooled. Therefore, it is possible to appropriately suppress the temperature rise in the sealed housing 1 due to the heat generated by the rotary pump 2, etc., and prevent adverse effects on the electric motor 3, electrical components, etc., so that high pump performance can be maintained and the device life can be maintained. Can be prolonged.

In addition, since all or most of the exhaust heat to the outside of the sealed housing 1 is mediated by the cooling liquid (cooling water) for heat exchange, heat dissipation to the surroundings can be minimized, and the installation environment can be improved. It has the advantage of having a very small impact. For example, it is possible to reduce the air conditioning burden in the room in which the package type rotary pump unit according to the present invention is installed.
Further, since the closed structure can be formed by the closed housing 1, there is an advantage that the driving noise reduction effect is large. According to the embodiment of the hermetically sealed structure with the hermetically sealed housing 1 according to this embodiment, the noise can be reduced to 73 dB.
By forming the closed structure by the closed housing 1 in this way, the inflow and outflow of gas between the inside of the housing and the outside world is sufficiently restricted, so that the dew water inside the housing is sufficiently restricted even in a high humidity environment. The amount of water generated is small. That is, if the coolant can be supplied, the internal temperature of the sealed housing 1 is not easily affected by the product installation environment (temperature / humidity), so that it can be used in a wide range of environmental temperature / humidity range.
As will be described later, in this embodiment, the first muffler portion 31 and the second muffler portion 32 are housed in the sealed housing 1, and the heat dissipated from these muffler portions is also included. It is configured to be able to cool the internal air of the sealed housing 1.

Further, in this embodiment, the circulating air inlet portion 25a, which is arranged inside the closed housing 1 and is provided so as to cover the rotary pump 2 and into which the internal air circulating inside the closed housing 1 is introduced, The pump cover portion 25 is provided so as to be provided with the circulating air outlet portion 25b from which the internal air including the heated air is discharged. The installation position of the blower 6 with respect to the pump cover portion 25 is limited to this embodiment as long as the internal air can flow so as to be introduced from the circulating air inlet portion 25a and discharged from the circulating air outlet portion 25b. It is also possible to selectively set it as appropriate, including the positional relationship with the liquid-cooled heat exchanger 5.

According to the pump cover portion 25, the heat generated by the rotary pump 2 can be retained inside the pump cover portion 25, and the heat is dissipated to the outside of the pump cover portion 25 to dissipate the heat to the outside of the pump cover portion 25 as a whole in the sealed housing 1. Dispersion in space can be suppressed. According to this, by not dispersing the heat from the rotary pump 2, the hot air (heated air) can be collected and sent to the liquid-cooled heat exchanger 5, and the heated air can be efficiently cooled. That is, the temperature difference between the heated air and the liquid-cooled heat exchanger 5 can be made larger, the heat exchange is efficiently performed, and the temperature rise in the closed housing 1 can be efficiently suppressed. Further, since the high-temperature air is collected and sent to the liquid-cooled heat exchanger 5, the circulating air outlet portion 25b has a narrowed flow path, and the liquid-cooled heat exchanger 5 can be miniaturized. It also reduces.

The pump cover portion 25 of this embodiment is an exhaust of the rotary pump 2 so that the internal air flows so as to effectively contact the entire outer surface of the rotary pump 2 so that the outer surface thereof can be efficiently cooled. On the side (the side opposite to the side to which the electric motor 3 is connected), a circulating air inlet portion 25a that surrounds the rotary pump 2 and is open in a band shape is provided. Then, the flow path is narrowed so that the circulating air outlet portion 25b from which the internal air including the heated air heated by the rotary pump 2 is discharged collects the internal air and guides it to the liquid-cooled heat exchanger 5. It has become. Further, in this embodiment, the circulating air outlet portion 25b is connected to the internal air introduction port in the heat exchange chamber of the liquid-cooled heat exchanger 5 in an airtight seal state. According to this, the flow of the internal air can be appropriately generated, the internal air can be appropriately circulated, the heat exchange can be efficiently performed, and the temperature rise in the sealed housing 1 can be efficiently suppressed.

Further, in this embodiment, the introduction port of the liquid-cooled heat exchanger 5 is connected to the side of the circulating air outlet portion 25b, and the blower device 6 sucks the internal air and circulates the air outlet portion from the circulating air inlet portion 25a. It is connected to the liquid-cooled heat exchanger 5 so as to flow through 25b and pass through the liquid-cooled heat exchanger 5. In this embodiment, the suction port for the internal air of the blower 6 is connected to the exhaust port for the internal air in the heat exchange chamber of the liquid-cooled heat exchanger 5 in an airtight seal state.

According to this, a smooth flow of the internal air can be generated rationally and effectively, the internal air can be circulated efficiently, heat exchange is efficiently performed, and the temperature inside the sealed housing 1 is achieved. The rise can be suppressed efficiently. Further, since the blower 6 is arranged in the liquid-cooled heat exchanger 5 as in the example of the present embodiment, the blower 6 itself sucks the air cooled by the liquid-cooled heat exchanger 5 and overheats. This can be prevented and the life of the device can be extended.
In this embodiment, the pump cover portion 25 (see FIGS. 3 to 6 and the like) is provided so as to cover the range of the pump chamber body portion 110 and the bearing body portion 120 (see FIGS. 13 to 18 and the like) of the rotary pump 2. Has been done. That is, as will be described later, it effectively covers the portion having a high surface temperature except for the first muffler portion 31 which is liquid-cooled. Further, 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 so that the circulating air inlet portion 25a is appropriately formed is set by the internal air. It suffices that the ventilation resistance at the time of flow does not increase as much as possible, and the internal air (heated air) heated by the heat generated by the rotary pump 2 is provided in a range where it is not dispersed to the outside of the pump cover portion 25 as much as possible.

Further, in this embodiment, the rotary pump 2 is a biaxial rotary pump, and one rotor rotary shaft (rotary shaft 20A) is connected and rotated in series with the rotary shaft 3a of the electric motor 3 to rotate the other rotor. A shaft (rotating shaft 20B) is provided so as to rotate in synchronization with one rotor rotating shaft (rotating shaft 20A) via a gear, and the other rotor rotating shaft (rotating shaft 20B) is arranged. In the space on the extension of the axis of the rotary shaft 20B, which is adjacent to the portion where the electric motor 3 and one rotor rotary shaft (rotary shaft 20A) are connected, the liquid-cooled heat exchanger 5 and the blower 6 is arranged.

According to this, the internal space of the closed housing 1 can be suitably used to circulate the internal air appropriately.
As shown in FIG. 4, the rotor rotary shaft (rotary shaft 20A) of this embodiment and the rotary shaft 3a of the electric motor 3 are connected in series via a coupling 3b. Further, as shown in FIG. 3 and the like, 3c is a safety cover, and covers the connection portion of the rotating shaft (3a, 20A) including the coupling 3b to be rotationally driven for safety. Further, the coupling 3b may be configured to blow air by attaching a blower blade coaxially with the rotation shaft (3a, 20A). According to this blower blade, the cooling performance can be improved.

Further, in this embodiment, the electric motor 3 is provided with a blower fan 7 for cooling the electric motor that blows air so as to cool the electric motor 3, and the blower fan 7 is one rotor rotating shaft (rotating shaft 20A). ) Is arranged on the rotation shaft on the opposite side to the side connected to) and is provided so as to blow air toward the motor body.

According to this, as shown by the thick arrow in FIG. 1, a smooth circulating flow of the internal air can be generated rationally and effectively, heat exchange is efficiently performed, and the inside of the sealed housing 1 is contained. The temperature rise can be suppressed efficiently. That is, as shown in FIG. 1, first, by being sucked by the blower 6, the internal air is heated through the inside of the pump cover portion 25 and then cooled through the liquid-cooled heat exchanger 5. .. Next, the internal air sucked from the liquid-cooled heat exchanger 5 is discharged by the blower device 6 in a direction away from the rotary pump 2 (to the left from the blower device 6 in FIG. 5), and is discharged to the side of the electric motor 3 (to the left from the blower device 6 in FIG. 5). It will flow on the upper side of the electric motor 3 in FIG. Next, the internal air cooled by the liquid-cooled heat exchanger 5 and discharged from the blower device 6 hits the inner surface of the sealed housing 1, and a part of the internal air is sucked by the blower fan 7 of the electric motor 3. It reverses and flows so as to cool the motor body of the electric motor 3, and then flows to the side of the body of the rotary pump 2. Then, the internal air flowing around the pump cover portion 25 is inverted and drawn from the circulating air inlet portion 25a into the inside of the pump cover portion 25 by the suction force of the blower device 6. As described above, when the air flow is generated, the internal air can be appropriately circulated, heat exchange can be efficiently performed, and the temperature rise in the sealed housing 1 can be efficiently suppressed.

Further, in the present embodiment, as shown in FIGS. 1, 9 and 10, the air in the switchboard 8 formed in the shape of a small chamber flows through the switchboard 8 formed on the front surface side of the sealed housing 1. As an air cooling means for cooling, a blower 9 for cooling electrical components is attached to the lower part of the switchboard 8.

According to the blower 9 for cooling electrical components of this embodiment, a part of the internal air (cooling gas) in the sealed housing 1 is sucked into the switchboard 8 from the bottom to the top in the switchboard 8. It can be made to flow and blown so as to be discharged from an upper opening (not shown) in the switchboard 8. As a result, it is possible to efficiently cool the electrical components 82 and the inverter device 83 having high heat generation installed in the switchboard 8. Further, the internal air discharged from the switchboard 8 is sucked into the inside of the pump cover portion 25 from the circulating air inlet portion 25a of the pump cover portion 25. As shown in FIGS. 9 and 10, 81 is an operation unit and has low heat generation. Therefore, in this embodiment, the air cooling means is not individually provided and is arranged at a position away from the switchboard 8.

Further, in this embodiment, as will be described in detail with reference to FIGS. 13 to 21, the rotary pump 2 is connected to the coolant supply source 4 so as to be liquid-cooled. In this embodiment, the coolant flowing from the coolant supply source 4 first passes through the liquid-cooled heat exchanger 5, and then cools the exhaust gas discharged from the exhaust port 55 (see FIG. 13 and the like). The pipes are connected in series. By liquid-cooling both the liquid-cooled heat exchanger 5 and the rotary pump 2 in this way, the temperature rise in the sealed housing 1 can be effectively suppressed.

Next, a specific example of the flow path related to the cooling liquid supplied from the cooling liquid supply source 4 will be described with reference to the drawings (FIGS. 1, FIG. 3, FIG. 7, FIGS. 9 to 15, etc.).
The coolant supply source 4 is connected to the coolant supply connection port 4a provided on the back surface of the sealed housing 1, and the coolant is cooled from the coolant supply connection port 4a by a liquid flow pump (not shown). First, it is supplied to the liquid-cooled heat exchanger 5 through the supply pipe 4b to cool the liquid-cooled heat exchanger 5. In the embodiment in which the electric rotary pump 200 is arranged in two stages shown in FIGS. 9 to 12, the coolant supply pipe 4b is branched into two, and the coolant is applied to each of the two stages of the electric rotary pump 200. It is configured so that it is supplied and the two coolant discharge pipes 4c are merged and the coolant is discharged.

Next, the coolant having cooled the internal air via the liquid-cooled heat exchanger 5 is connected to the coolant inlet in order to cool the rotary pump 2 through the coolant connection pipe 5b (see FIGS. 1, 7, etc.). It is supplied to the unit 71a (see FIGS. 7, 15, etc.). Then, the coolant passes through the bearing portion coolant flow path 71 as described later based on FIGS. 13 to 21, so that the bearing portion 40 and the gearbox 45 of the rotary pump 2 are cooled, and the gearbox is cooled accordingly. The lubricating oil in 45 is cooled.

Next, the coolant that has passed through the bearing portion coolant flow path 71 is introduced into the exhaust section coolant flow path 72 and cools the exhaust of the rotary pump 2, as will be described later based on FIGS. 13 to 21. It flows, passes through the extension portion coolant flow path 73, cools the portion of the rotary pump 2 that constitutes the first muffler portion 31, and is discharged from the extension portion coolant outlet connection portion 73b. A coolant discharge pipe 4c is connected to the extension portion coolant outlet connection portion 73b, and the outlet end of the coolant discharge pipe 4c serves as a coolant discharge connection port 4d connected to the coolant supply source 4. There is.

By flowing through the above flow path, the liquid-cooled heat exchanger 5 and the rotary pump 2 can be cooled, and the cooling liquid that cools the internal air of the sealed housing 1 and the lubricating oil and exhaust of the rotary pump 2 can be used. In this embodiment, the liquid is returned to the coolant supply source 4 and circulated. Of course, when using groundwater or the like, it may flow in one direction without circulating.

According to this, the liquid-cooled heat exchanger 5, the bearing portion 40 of the rotary pump 2, and the gearbox 45 are provided by the cooling liquid flowing through the liquid-cooled flow path connected in series to the liquid-cooled heat exchanger 5 and the rotary pump 2. The three locations of the first muffler portion 31, which is the exhaust portion of the rotary pump 2, can be rationally cooled in order. That is, with respect to the temperature of each part, the permissible temperature of the oil stored in the gearbox is higher than the permissible temperature of the internal air of the sealed housing 1, and the permissible temperature of the oil stored in the gearbox is compared. Since the temperature relationship is such that the permissible temperature of the exhaust of the rotary pump is even higher, it is rational to flow the coolant in the above-mentioned order. That is, when the above-mentioned three locations are sequentially cooled, the coolant is gradually heated, but in each portion, the temperature difference that can be sufficiently cooled (the temperature difference between the coolant temperature and the temperature of the cooled portion). Can be maintained. Further, such a liquid-cooled pipe connected in series has an advantage that the configuration of the pipe can be simplified and the cost can be reduced.
The liquid cooling pipe is not limited to this embodiment, and may be provided in parallel. By piping in parallel, it is possible to adjust the flow rate individually, and there is an advantage that precise cooling control can be performed.

Next, specific measurement data (verification values) of the cooling effect in the closed housing 1 of the embodiment shown in FIGS. 1 to 7 will be described.
Data was obtained by setting the temperature of the coolant (cooling water) to 32 ° C. as an example of the condition of the highest assumed temperature and measuring the temperature of each part.
As comparative data, when the liquid-cooled heat exchanger 5 is not installed and the rotary pump 2 is provided as in the embodiment shown in FIGS. 13 to 21 and water-cooled, the internal air of the sealed housing 1 becomes. It rose to 80 ° C.
On the other hand, when the rotary pump 2 is water-cooled as described above and the liquid-cooled heat exchanger 5 is installed to water-cool the internal air as in the example of the present embodiment, the circulating air outlet portion 25b of the pump cover portion 25 is used. The temperature of the internal air in the above was 55 ° C., and the temperature of the internal air that passed through the liquid-cooled heat exchanger 5 and was discharged from the blower 6 and circulated to the electric motor 3 and the switchboard 8 became 45 ° C. As a result, the heat resistant temperature of the electric motor 3 and the electrical component 82 could be sufficiently cleared. Further, the temperature of the cooling water returned to the coolant supply source 4 became 40 to 45 ° C.

By the way, the intake pipe of the rotary pump 2 is provided so that the intake introduction pipe connection port 16 can be connected to the external intake pipe, and the outside air can be taken in through the external intake pipe. Has been done. Further, the check valve 17 is connected between the intake inlet pipe connection port 16 and the intake port 15 of the rotary pump 2, so that the flow of gas from the pump 2 to the intake introduction pipe connection port 16 can be regulated. It is provided.
Further, reference numeral 90 denotes a drain discharge connection port, which is a discharge port capable of discharging the drain to the outside. A drain pan 91 arranged under the rotary pump 2 and a heat exchanger drain pan 93 arranged in the liquid-cooled heat exchanger 5 are connected to the drain discharge connection port 90 by a drain pipe 92 or a heat exchanger drain pipe 94. It is possible to receive the generated drain and discharge it appropriately.

Next, the muffling structure of the package type rotary pump unit according to the present invention will be described in detail with reference to the attached drawings (FIGS. 1 to 21). As described above, the package type rotary pump unit according to the present invention has, as a basic configuration, an electric rotary pump 200 including a rotary pump 2 for sucking and exhausting gas and an electric motor 3 for driving the rotary pump 2, and an electric rotary pump thereof. It is provided with a closed housing 1 containing a pump 200.

The rotary pump 2 mounted on the package type rotary pump unit according to the present invention has an exhaust cooling unit in which the exhaust is cooled by the coolant supplied from the coolant supply source 4 arranged outside the sealed housing 1. A first muffler portion 31 that also serves as a sound deadening effect is provided. A second muffler portion 32 that introduces exhaust gas that has passed through the first muffler portion 31 to muffle the sound is arranged above the electric rotary pump 200 inside the sealed housing 1.

According to the package type rotary pump unit according to the present invention, when the rotary pump 2 is built in the closed housing 1, the noise generated by the operation of the rotary pump 2 is reduced more rationally and effectively. It has a special advantageous effect of being able to do it. That is, by providing the first muffler portion 31 in which the exhaust of the rotary pump 2 is cooled by the coolant and arranging the second muffler portion 32 above the electric rotary pump 200, the electric rotary pump 200 and the muffler ( The entire first muffler portion 31 and the second muffler portion 32) can be effectively covered with the above-mentioned closed type housing (sealed housing 1). Therefore, the noise can be shielded and absorbed, including the sound leaking from the muffler, the piping in the middle, and the like, and the muffling effect can be effectively enhanced. The second muffler portion 32 itself arranged 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 according to this embodiment, the noise can be reduced to 73 dB, and high quietness can be realized. Further, by arranging the second muffler portion 32 on the upper part of the electric rotary pump 200, the foot space can be suppressed. Of course, in order to improve the sound absorbing performance, the sound absorbing material may be attached to the inner surface of the member constituting the sealed housing 1.

Further, in this embodiment, the second muffler unit 32 is composed of a plurality of sound reduction chambers, and the plurality of sound reduction chambers are in the same direction as the connection direction of the rotary pump 2 and the electric motor 3 and are sealed. It is provided so as to be arranged in series in the longitudinal direction of the body 1.

According to this, a plurality of sound reduction chambers can be suitably arranged in a limited space, and a sufficient sound reduction effect can be obtained. That is, since the electric rotary pump 200 of this embodiment is in the form of connecting the rotary pump 2 and the electric motor 3 in series, it has a horizontally long shape, and the sealed housing 1 is also horizontally long as in this embodiment. It is formed. The second muffler portion 32 can be appropriately arranged inside the horizontally long sealed housing 1 so as to follow the form of the electric rotary pump 200, and the overall configuration can be compactly provided. ..

As the internal structure of the second muffler portion 32, a form for enhancing the sound reduction (silence) effect by expansion, shielding, sound absorption, etc. can be appropriately and selectively designed. For example, by setting three sound reduction chambers and arranging the three chambers in series, a compact structure with high sound reduction performance can be obtained.
More specifically, for example, in this embodiment, the second muffler portion 32 has a tubular outer shape that is long in the axial direction, and the sound reduction chamber and the intermediate portion on one end side in the longitudinal direction thereof. The sound reduction chamber and the sound reduction chamber on the other end side are provided, and in the sound reduction chamber on the one end side, the exhaust introduced by the exhaust pipe extended from the exhaust port 57 of the first muffler portion is exhausted. Sound is reduced by discharging the sound so that it is inflated from the part that is a perforated pipe on the tip side of the pipe. Then, the pipeline is communicated so that the exhaust gas is sent from the sound reduction chamber on the one end side to the sound reduction chamber on the other end side, and the exhaust gas is discharged to the sound reduction chamber on the other end side to reduce the sound by expansion. Let me. Further, the exhaust gas introduced into the sound reduction chamber on the other end side is described via a ventilation hole provided in a partition wall between the sound reduction chamber on the other end side and the sound reduction chamber in the intermediate portion so as to reverse the exhaust gas. The sound is reduced by expansion by discharging the exhaust to the sound reduction chamber in the middle portion, and the exhaust is provided so that the exhaust can be discharged from the sound reduction chamber in the middle portion to the outside through the exhaust discharge port 35 of the second muffler portion. Has been done.

Further, in this embodiment, the second muffler portion 32 is installed in a state of being suspended inside the sealed housing 1. That is, as shown in FIGS. 3 and 9, the second muffler portion 32 formed in the cylindrical shape of this embodiment is fixed to the upper part of the housing frame portion 1a and extends downward. It is fixed to 37 and is installed in a state of being suspended inward from the upper part of the sealed housing 1.

According to this, by utilizing the space above the electric rotary pump 200, the muffler has an appropriate volume having a high sound deadening effect due to expansion and is lighter than other constituent devices (second muffler portion 32). Can be arranged appropriately and easily. Of course, by appropriately attaching a sound absorbing material to the inner surface of each of the above-mentioned sound reducing chambers of the second muffler portion 32, a sound deadening effect due to sound absorption can be obtained.

Further, in this embodiment, as shown in FIGS. 3, 4, 7, and 9 to 12, the electric rotary pump 200 is installed in the closed housing 1 via the vibration damping member 300, and is the first. The muffler portion 31 and the second muffler portion 32 are connected via a vibration buffer pipe 33. That is, in this embodiment, the electric rotary pump 200 is installed on the base portion 1b in the sealed housing 1 via the vibration damping member 300 provided with the vibration-resistant rubber, and the exhaust port 57 and the second exhaust port 57 of the first muffler portion. A vibration buffer pipe 33 is connected to the exhaust introduction port 34 of the muffler portion of the above, and is provided so that the exhaust flows from the first muffler portion 31 to the second muffler portion 32.

According to this, since the electric rotary pump 200 is installed by the vibration damping member 300 and is connected to the second muffler portion 32 by the vibration buffer pipe 33, the vibration of the electric rotary pump 200 is sealed. It is possible to reduce transmission to the side of the housing 1, and it is possible to suitably obtain vibration-proof and sound-proof effects. Further, since the vibration of the electric rotary pump 200 can be reduced from being transmitted to the second muffler portion 32, the second muffler portion 32 can be appropriately and more easily installed in the sealed housing 1.

Further, in this embodiment, as shown by the package type rotary pump unit in which the electric rotary pump 200 is mounted on a plurality of stages (two stages in this embodiment) shown in FIGS. 8 to 12, the second muffler portion 32 is provided. It is arranged on the back side inside the sealed housing 1, and the switchboard 8 is arranged on the front side. According to this, the switchboard 8 serves as a shielding portion, and the noise transmitted to the front side can be further reduced. This can further improve the working environment.

Next, as an example of the rotary pump used in the package type rotary pump unit according to the present invention, a morphological example of the claw pump will be described with reference to FIGS. 13 to 21.
In this claw pump, as shown in FIG. 13 and the like, 110 is a pump chamber body portion, and a cylinder is formed so as to form a pump chamber 10 (see FIG. 22) having a cross-sectional shape in which a part of two circles is overlapped. It includes a 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.

Further, the two rotating shafts 20A and 20B are arranged in parallel in the pump chamber 10 and are provided so as to be rotated at the same speed in opposite directions by a pair of gears 21A and 21B. In this embodiment, the two rotary shafts 20A and 20B are integrally fixed with gears 21A (drive side gears) and 21B (driven side gears), respectively. The pair of gears 21A and 21B are meshed in a gear box 45 configured by the bearing body portion 120.

Further, two rotors 30A and 30B are provided in the pump chamber 10 corresponding to the two rotating shafts 20A and 20B, and can be rotated in a non-contact state with each other to compress and exhaust the inhaled gas. A hook-shaped claw portion (see FIG. 22) is formed and provided as described above. Then, one end wall portion 10b of the pump chamber body portion 110 is located on the side of the gear box 45 containing the pair of gears 21A and 21B, and the gas is discharged to at least the other end wall portion 10c of the pump chamber body portion 110. The exhaust port 55 is provided. As a result, a package type rotary pump unit, which is a kind of twin-screw rotary pump, is configured.

In this embodiment, the two rotors 30A and 30B are arranged so as to correspond to one end (one end) of each of the two rotary shafts 20A and 20B and are supported in a cantilever state. 20B is bearing by the bearing portion 40, one end wall portion 10b of the pump chamber body portion 110 is located on the side of the bearing portion 40, and an exhaust port for discharging gas to the other end wall portion 10c of the pump chamber body portion 110. 55 is provided. Reference numeral 15 is an intake port, which is opened at a position in the pump chamber 10 facing a portion where the gas is not compressed. The intake port 15 of this embodiment is provided at a corner portion of the upper portion of the pump chamber body portion 110, and is provided in a form notched over the upper wall portion of the cylinder portion 10a and the upper portion of one end wall portion 10b. Has been done. Further, reference numeral 14 denotes an intake connection port, the lower end thereof is connected to the intake port 15, and the upper end is provided so as to be connected to a pneumatic device (not shown) via a pipeline.

Then, in the package type rotary pump unit according to the present invention, the exhaust gas for passing the cooling liquid to the side of the other end wall portion 10c of the pump chamber body portion 110 so as to cool the exhaust gas discharged from the exhaust port 55. A unit coolant flow path 72 is provided. In this embodiment (example when used as a vacuum pump), the state in which the exhaust is discharged from the exhaust port 55 means that the pump chamber 10 communicates with the outside air (air) and is open. It is a state, and its exhaust will be released into the atmosphere (air). The liquid of the coolant is typically cooling water, but of course, other liquids other than water can be used, including a mixed liquid (aqueous solution) with water such as antifreeze, oil, and the like. be.

According to the package type rotary pump unit according to the present invention, the pump chamber 10 is overheated even when the pump is used as a vacuum pump in a high vacuum range where the ultimate vacuum is closer to the absolute vacuum. It can be prevented more positively and effectively, and the pump performance can be significantly improved.

That is, by providing the exhaust section coolant flow path 72 on the side of the other end wall portion 10c of the pump chamber body portion 110, it is possible to effectively cool the exhaust immediately after being discharged from the exhaust port 55 by the coolant. can. According to this, even if the vacuum pump is used in a range where the degree of vacuum is higher than a certain level and is heated by the backflow of exhaust gas, it is possible to suppress an increase in the internal temperature of the pump chamber 10. Therefore, it is possible to set a small clearance that makes the inner surface of the wall of the pump chamber 10 and the two rotors 30A and 30B non-contact, and it is possible to reduce gas leakage due to the clearance, so that the pump efficiency can be improved. Can be improved.

Further, according to the package type rotary pump unit according to the present invention, since the clearance can be set small as described above, the ultimate vacuum degree can be further increased, and overheating can be prevented even if there is a backflow of the exhaust, so that the exhaust can be exhausted. The opening area of the port 55 can be set wider, and a vacuum pump having a larger processing air volume can be configured.

Then, according to the package type rotary pump unit of the present embodiment, the side of the other end wall portion 10c provided with the most heated exhaust port 55 is locally and positively cooled. There is. That is, the other wall portion of the wall portion of the pump chamber body portion 110 centered on the exhaust port 55 so as to reduce the temperature difference with respect to the pump chamber body portion 110 in which a large temperature gradient (temperature difference) occurs. The exhaust is cooled by giving priority to the 10c side for cooling. By cooling the exhaust gas in this way to prevent overheating of the pump chamber 10, it has been confirmed in the examples that the internal temperature difference is reduced by about 140 ° C. and that the ultimate vacuum degree is increased to 97 kPa. The pump performance can be significantly improved. Conventionally, the ultimate vacuum degree is up to about 90 kPa in order to avoid contact (internal interference) between the inner surface of the wall of the pump chamber 10 and the two rotors 30A and 30B as a limit for continuous ultimate operation. I could only drive. On the other hand, according to the present invention, the deadline operation having a higher ultimate vacuum degree can be continuously performed.

By the way, in the package type rotary pump unit, since the compression rate of the gas is high and the gas is heated and exhausted, the portion of the exhaust port 55 is most likely to be overheated, and the other end wall portion on which the exhaust port 55 is formed is formed. The portion of 10c becomes hotter than the other portions. The temperature of the other portion of the pump chamber body portion 110 is lower than that of the other end wall portion 10c. Therefore, if the pump chamber body portion 110 including the cylinder portion 10a and the like is cooled in the same manner as a whole, the temperature difference between the exhaust port 55 of the other end wall portion 10c and another portion is maintained. The problem that the rotors 30A and 30B, which are the moving parts, interfere with each other due to the thermal expansion cannot be solved.

Further, according to the present embodiment, a coolant introduction port 72b (see FIG. 20) for introducing the coolant into the exhaust section coolant flow path 72 is provided in the vicinity of the exhaust port 55, and the exhaust section coolant flow path 72 is provided. The formed portion is provided with a cooling liquid flow regulating unit 61b that regulates the flow of the introduced cooling liquid so that the cooling liquid circulates in the vicinity of the exhaust port 55 in advance. As shown in FIG. 20, the cooling liquid flow regulating section 61b of the present embodiment has a plurality of locations (two locations in this embodiment) of the cooling liquid flow path forming surface 61a of the first flow path forming section 61, which will be described later. It is provided in the form of a rib-like protrusion.

According to this, the exhaust immediately after the exhaust port can be effectively cooled by cooling the portion (around the exhaust port 55) centered on the exhaust port 55, which is the most heated part of the pump chamber body portion 110. By lowering the temperature around the exhaust port 55 and the exhaust port, it is possible to suppress excessive heating around the exhaust port 55 and biased deformation due to thermal expansion in a well-balanced manner. As described above, since the thermal expansion of the pump chamber body portion 110 and the two rotors 30A and 30B can be suppressed in a well-balanced manner, the mutual clearance between them can be reduced and the pump efficiency can be improved.

In the package type rotary pump unit, the exhaust port 55 is generally provided at a portion corresponding to the lower portion of the pump chamber 10 (in this embodiment, the lower portion of the other end wall portion 10c) from the viewpoint of drive stability. become. Then, in this embodiment example, the coolant introduction port 72b is arranged as described above, and the portion near the exhaust port 55 located at the lower part of the other end wall portion 10c of the exhaust section coolant flow path 72 is further formed. The cooling liquid is cooled in advance with a cooling liquid having a low temperature, and the cooling liquid thus cooled at the other end wall portion 10c is discharged upward so as to pass through the exhaust portion cooling liquid outlet connecting portion 72d. At this time, the coolant exchanges heat and the temperature rises, so that the specific gravity becomes smaller and a vector of an upward flow is generated. According to the flow of the coolant, the portion of the lower exhaust port 55 can be effectively cooled, and the direction of the flow due to the temperature rise of the coolant and the direction of the flow for discharging the coolant upward can be determined. Can be aligned. Therefore, the cooling liquid can be passed smoothly, and the cooling efficiency can be effectively improved.

Further, according to the present embodiment, the exhaust liquid flow path 72 is arranged on the other end wall portion 10c of the pump chamber body portion 110 so as to cover the outer surface side of the other end wall portion 10c. A first flow path forming portion 61 including a coolant flow path forming surface 61a provided so as to form the exhaust part cooling liquid flow path 72 between the portion and the outer surface of the other end wall portion 10c. Is provided by being arranged. According to this, the exhaust liquid flow path 72 can be effectively and rationally configured.

As shown in FIGS. 13, 20, and 21, the first flow path forming portion 61 of this embodiment is provided by a disc-shaped member having irregularities formed so that flow paths are formed on both sides. It is fixed to the outer surface of the other end wall portion 10c by a bolt, and is provided so that the mating portion is watertightly sealed by the sealing member 65 to form the exhaust section coolant flow path 72. The mating portion of this embodiment is an inner loop mating portion 61c formed in a rectangular loop frame shape surrounding the exhaust port 55 so as to extend the exhaust passage of the exhaust port 55, and a peripheral portion of the other end wall portion 10c. It is composed of an outer loop mating portion 61d formed so as to abut in a loop frame shape. An exhaust section coolant flow path 72 is formed between the inner loop mating portion 61c and the outer loop mating portion 61d to fill the cooling liquid. According to this, the cooling liquid is entirely brought into contact with the outer wall surface of the other end wall portion 10c so that the cooling liquid can be efficiently cooled. Further, this structure has a compact structure in which the layered exhaust section coolant flow path 72 is stacked in a plane on the outside of the outer end surface of the pump chamber body portion 110.

Further, in the first flow path forming portion 61 of the present embodiment, one of the exhaust liquid flow paths 72 is formed on the coolant flow path forming surface 61a, which is a surface (facing) facing the outer surface of the other end wall portion 10c. The passage forming wall constituting the cooling liquid flow regulating portion 61b is provided in a protruding form so that the exhaust port peripheral flow path portion 72c, which is a portion and is a groove-shaped passage, is formed. That is, in this embodiment, the outer surface of the other end wall portion 10c is a flat surface, and as shown in FIGS. 13 and 20, it is on the side of the coolant flow path forming surface 61a of the first flow path forming portion 61. A passage forming wall (cooling liquid flow regulating part 61b) for appropriately bending and guiding the exhaust liquid flow path 72 is provided. The present invention is not limited to this, and it is also possible to appropriately provide a passage forming wall on the outer surface side of the other end wall portion 10c.

Further, according to the present embodiment, the surface of the first flow path forming portion 61 is opposite to the coolant flow path forming surface 61a so that the exhaust gas is cooled by the first flow path forming portion 61. An exhaust flow path 56 through which exhaust gas passes is provided on the side of the exhaust flow path forming surface 61e, which is the outer surface of 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 passes.

According to the exhaust flow path 56, the superheated exhaust can be effectively cooled, and the temperature inside the pump chamber 10 is lowered by lowering the temperature of the exhaust, and the pump chamber body portion 110 forming the pump chamber 10 or the like. It is possible to prevent the two rotors 30A and 30B from being overheated and thermally expanding in a well-balanced manner.
Further, the exhaust flow path 56 can appropriately regulate the direction of the exhaust flow, has a form for promoting cooling of the exhaust, and also has a muffler structure for reducing the exhaust noise. It has become. That is, the first muffler portion 31 is configured by the structure in which the exhaust flow path 56 is formed. Reference numeral 57 is an exhaust port of the first muffler portion, which is provided by being opened in the upper wall portion of the first flow path forming portion 61 and serves as an exhaust port of the exhaust flow path 56. It is exhausted to the outside by the exhaust port 57 of the muffler portion. As shown in FIG. 21, the exhaust port 57 of the first muffler portion of this embodiment is provided in a shape in which the flow path is narrowed on the inner side, and is formed so as to enhance the sound deadening effect.

Further, according to the present embodiment, the exhaust flow path 56 is a portion arranged in the first flow path forming portion 61 so as to cover the outer surface side of the first flow path forming portion 61. By arranging the second flow path forming portion 62 provided with the exhaust flow path forming surface 62a provided so as to form the exhaust flow path 56 with the outer surface of the first flow path forming portion 61, the second flow path forming portion 62 is arranged. It is provided. According to this, the exhaust flow path 56 can be effectively and rationally configured, and the exhaust immediately after the exhaust port can be effectively cooled on both the exhaust flow path forming surface 61e and the exhaust flow path forming surface 62a. .. Further, this structure has a compact structure in which the layered exhaust flow paths 56 are stacked in a plane on the outside of the outer end surface of the pump chamber body portion 110.

As shown in FIG. 13, the second flow path forming portion 62 of the present embodiment is an exhaust flow path forming surface which is an inner surface (a surface abutting on the outer surface side of the first flow path forming portion 61). The 62a is provided by a flat plate-shaped member, and is fixed to the outer surface (exhaust flow path forming surface 61e) side of the first flow path forming portion 61 by a bolt. Further, with respect to the exhaust flow path forming surface 62a (flat surface), on the side of the outer surface (exhaust flow path forming surface 61e) of the first flow path forming portion 61, there is a groove shape that becomes the exhaust flow path 56. The exhaust passage forming wall 61f is provided in a protruding form so that the passage is formed. Then, the loop frame-shaped mating portion 61g and the exhaust passage forming wall 61f on the outer peripheral portion on the outer surface side of the first flow path forming portion 61 and the inner surface of the second flow path forming portion 62 are substantially brought into close contact with each other. It can be made airtight, or a sealing member can be arranged to make it airtight. The present invention is not limited to this, and it is also possible to provide an exhaust passage forming wall on the side of the exhaust passage forming surface 62a. Further, as shown in FIG. 21, since the exhaust flow path 56 is formed in a complicatedly bent flow path, the cooling of the exhaust can be further promoted, and the exhaust flow path 56 functions appropriately as a muffler chamber to improve the exhaust noise. It can be reduced.

Further, according to the present embodiment, the extension cooling liquid flow path 73 continuous with the exhaust cooling liquid flow path 72 is formed on the second flow path forming portion 62 on the outer surface of the second flow path forming portion 62. The extension passage cooling liquid flow path is a portion arranged so as to cover the side of the extension flow path forming surface 62b) and is connected to the outer surface (extension flow path forming surface 62b) of the second flow path forming portion 62. It is provided by arranging a third flow path forming portion 63 including an extension flow path forming surface 63a provided so as to form 73. According to this, the extension cooling liquid flow path 73 can be effectively and rationally configured. Further, this structure has a compact structure in which the layered extension cooling liquid flow path 73 is stacked in a plane on the outside of the outer end surface of the pump chamber body portion 110. Further, according to the layered extension coolant flow path 73 and the structural wall constituting the layered extension, noise can be reduced. That is, the structure forming the extension portion coolant flow path 73 and the exhaust section coolant flow path 72 described above has a structure that shields sound and reduces noise, and is a component of the first muffler portion 31. It is also.

As shown in FIG. 13, the third flow path forming portion 63 of the present embodiment is provided by a flat flat plate-shaped member (plate member), and the second flow path forming portion 62 is provided by a bolt. It is fixed to the outer surface side of the second flow path forming portion 62, and the peripheral edge mating portion 62c provided in a loop frame shape on the outer surface of the second flow path forming portion 62 is watertightly sealed by the seal member 65 so that the extension portion coolant flow path 73 is formed. It is provided in. Further, in this embodiment, the extension cooling liquid flow path 73 is configured to retain the cooling liquid in a flat layered space, but the present invention is not limited to this, and is not limited to this. Of course, the flow path may be set in. Further, it is also possible to improve the cooling performance by forming the extension coolant flow path 73 in multiple layers. Further, also in the extension portion coolant flow path 73, similarly to the exhaust portion coolant flow path 72, in the upper part of the second connection pipe 72e so that the coolant flows so as to generate a flow from the lower part to the upper part. The second connection from the exhaust part coolant outlet connection part 72d provided and connected to the exhaust part coolant flow path 72 to the extension part coolant inlet connection part 73a provided in the lower part of the second connection pipe 72e. An extension coolant outlet connection portion 73b is provided at the upper part so that the coolant that is communicated through the pipe 72e and flows through the extension portion coolant flow path 73 is discharged to the outside.

By the way, in this embodiment, the pump chamber 10 is a cylinder case 11 in which a cylinder portion 10a, one end wall portion 10b, and one structural wall portion 121a provided with a first bearing portion 40a are integrally provided. , The side plate 12 provided as the other end wall portion 10c is fixed in a sealed state. As described above, in this embodiment, the pump chamber 10 is formed by a member divided into two, but is not limited to this, for example, the cylinder portion 10a, one end wall portion 10b, and the other end wall portion 10c. Of course, it may be formed mainly by a member divided into three parts.

Next, a morphological example of the configuration for cooling the bearing portion 40 bearing the two rotary shafts 20A and 20B in the twin-screw rotary pump according to the present invention will be described in detail with reference to the attached drawings (FIGS. 13 to 21). do. The biaxial rotary pump of the present embodiment is a package type rotary pump unit as described above, but the present invention is not limited to this, and other biaxial rotary pumps such as roots pumps and screw pumps. It can also be applied to pumps. Further, the biaxial rotary pump according to the present invention is not limited to the mode in which the two rotors 30A and 30B are bearing and supported in a cantilever state as in the example of the present embodiment, and the rotary shafts 20A and 20B are rotated at both ends. It has a configuration that can be applied to a biaxial rotary pump that can be freely bearing.

In the biaxial rotary pump according to the present invention, as shown in FIG. 13, a structural wall portion 121 provided with a bearing portion 40 bearing the two rotary shafts 20A and 20B is configured, and the two rotary shafts 20A and 20B are provided. A bearing body portion 120 that constitutes a structural wall portion 121 as a gear box 45 that includes a pair of gears 21A and 21B that are provided and mesh with each other is provided. In the bearing body portion 120 of this embodiment, the two rotors 30A (driving side rotor) and 30B (driven side rotor) have two rotating shafts 20A (driving side rotating shaft) and 20B (driven side rotating shaft). A bearing portion 40 for bearing the rotating shafts 20A and 20B is provided so as to be arranged at one end and supported in a cantilevered state. The bearing body portion 120 and the pump chamber body portion 110 constitute a pump body 100 of a biaxial rotary pump.

Then, the pump body 100 has the pump chamber body 110 and the bearing body 120 so that a cooling gap 60 capable of suppressing heat conduction is formed between the pump chamber body 110 and the bearing body 120. The bearing portion is cooled so that the coolant can be passed through the structural wall portion 121 (in this embodiment, one of the structural wall portions 121a) located on the side of the pump chamber body portion 110 of the bearing body portion 120. A liquid flow path 71 is provided.

According to this, the cooling liquid passing through the bearing portion cooling liquid flow path 71 has a heat transfer preventing effect of reducing the heat transfer of the compressed gas (exhaust) generated by driving the two rotors 30A and 30B to the bearing body portion 120. Due to the cooling effect of the above, the functional parts constituting the bearing portion 40 and the like can be extended in life, which is a special advantageous effect. That is, according to the present invention, by partitioning the pump chamber body portion 110 and the bearing body portion 120 and providing a cooling gap 60, heat conduction can be suppressed so that the amount of heat transfer is minimized, and the bearing portion can be suppressed. Since the bearing body portion 120 can be cooled more positively by the cooling liquid passing through the cooling liquid flow path 71, the reliability of the device can be improved. In this embodiment, it has been confirmed that the temperature rise of the lubricating oil can be reduced by about 40 ° C.
The functional component is a component including the bearing 41 and the oil seal 42, and is treated as a consumable component. By extending the life of these functional parts, running costs can be reduced.

By the way, the bearing portion 40 of the present embodiment is a pump chamber body portion 110 in the bearing body portion 120 so as to pivot the two rotating shafts 20A and 20B between the two gears 21A and 21B and the two rotors 30A and 30B. A drive motor (electric motor 3 (FIG. 3)) which is a first bearing portion 40a provided on the side structural wall portion (one structural wall portion 121a) and a structural wall portion opposite to the first bearing portion 40a. Etc.))) is a structural wall portion (the other structural wall portion 121b) arranged on the side to be connected, and is composed of a second bearing portion 40b provided so as to bearing the two rotating shafts 20A and 20B. ing. The rotary shaft 3a of the electric motor 3 is connected to the rotary shaft 20A (drive side rotary shaft) via a coupling 3b (see FIG. 4 and the like).

Further, in this embodiment, the lubricating oil is provided in a horizontal type installed by horizontally arranging the two rotating shafts 20A and 20B, and the bearing portion cooling liquid flow path 71 is stored in the gear box 45. Is provided at the lower part of the structural wall portion 121 of the bearing body portion 120 so as to pass below the liquid level of the lubricating oil in a stationary state so as to cool the bearing body portion 120. The stationary liquid level of the lubricating oil is set so as to be located between the inner bottom surface of the gear box 45 (oil chamber) and the rotating shafts 20A and 20B arranged horizontally. According to this, the lubricating oil can be effectively cooled, and the lubricating oil is scraped up by the two rotating gears 21A and 21B to lubricate the gears 21A and 21B and the bearing 41 and in the gearbox 45. Can be cooled.

In this embodiment, the bearing portion coolant flow path 71 is linearly arranged at the lower portion of the first bearing portion 40a in the bearing body portion 120 (below the bearing 41 of the first bearing portion 40a). It is provided in the shape of a through hole and is locally arranged. According to this, there is an effect that the portion of the bearing body portion 120 where heat conduction from the pump chamber body portion 110 side is likely to be easily cooled can be positively cooled and the lubricating oil can be effectively cooled.

Further, in this embodiment, the exhaust port 55 of the pump chamber 10 is provided at the lower part of the pump chamber body portion 110. According to this, when the bearing portion cooling liquid flow path 71 is provided at the lower part of the structural wall portion 121 of the bearing body portion 120 as described above, heat conduction is effectively suppressed and the bearing portion 40 is provided. It is possible to prevent overheating.

Further, in addition to the configuration provided in the horizontal type installed by horizontally arranging the two rotating shafts 20A and 20B as in the example of this embodiment, the cooling gap 60 is provided from the lower side to the upper side. A ventilation means for flowing air may be provided. According to this, the pump chamber body portion 110 and the bearing body portion 120 can be effectively air-cooled, and the reliability of the biaxial rotary pump can be further improved. That is, since the cooling air can be appropriately flowed between the pump chamber body portion 110 and the bearing body portion 120, heat transfer can be suppressed more effectively, and cooling by heat dissipation can be promoted. As a result, the temperature rise of the bearing body portion 120 can be suppressed, and the life of the functional component can be extended.

Then, according to the biaxial rotary pump of the present invention, the bearing portion coolant flow path 71 is provided in the pump chamber body portion 110 so that the coolant that has cooled the bearing body portion 120 cools the pump chamber body portion 110. It can be characterized by being connected to the cooling liquid flow path. According to this, the temperature of the cooling liquid flowing through the cooling liquid flow path 71 of the bearing portion is higher than that of the cooling liquid flow path provided in the pump chamber body portion 110 so that the lubricating oil does not boil and overheat. The temperature can be lower than the temperature of the flowing coolant, and the coolant can be effectively used.

Further, in this embodiment, the exhaust part coolant flow path 72 is connected to the bearing part coolant flow path 71 so that the coolant flows in the order of the bearing part coolant flow path 71 to the exhaust part coolant flow path 72. Has been done. According to this, the structural wall portion 121 (one of the structural wall portions) constituting the bearing portion 40 (first bearing portion 40a) of the bearing body portion 120 by one coolant supply source 4 (FIGS. 1 and 2). 121a) and the side of the other end wall portion 10c of the pump chamber body portion 110 can be directly and effectively cooled directly in sequence. The coolant of this embodiment is supplied from the coolant supply source 4 (FIGS. 1 and 2), and the coolant inlet connection portion 71a (FIG. 15, FIG. 17, FIG. 19) and the bearing portion coolant flow path 71. (FIG. 13, FIG. 19), the bearing portion coolant outlet connecting portion 71b (FIG. 14, FIG. 16, FIG. 18, FIG. 19) flows in this order, and the first connecting pipe 71c (FIG. 14, FIG. 16, FIG. 18). , FIG. 19), the exhaust section coolant inlet connection section 72a (FIG. 14, FIG. 16, FIG. 18), the coolant introduction port 72b (FIG. 20), and the exhaust section coolant flow path 72 (FIG. 13, FIG. 20). ), Flows through the extension coolant flow path 73, and is discharged to the outside of the pump 2. Not limited to this, it is of course possible to supply the cooling liquid separately without connecting the bearing portion cooling liquid flow path 71 and the exhaust section cooling liquid flow path 72, and the supply of the cooling liquid is adjusted individually. It may be optimized by doing so.

Further, in the flow path composed of the bearing part cooling liquid flow path 71, the exhaust part cooling liquid flow path 72, and the extension part cooling liquid flow path 73 of this embodiment, the exhaust part is above the bearing part cooling liquid flow path 71. The coolant flow path 72 is arranged, and the coolant flow path 72 in the exhaust section and the coolant flow path 73 in the extension section are configured so that the coolant flows from the bottom to the top, and the direction of flow due to the temperature rise of the coolant. By aligning the properties and the direction of the flow of the cooling liquid, the cooling liquid can flow smoothly, and the bearing portion 40 and the exhaust can be effectively cooled.

According to the cooling structure of the twin-screw rotary pump described above, the cooling performance can be rationally corresponding to the package type rotary pump unit, and the pump performance can be improved. Further, in the package type rotary pump unit according to the present invention, the lower side of the pump chamber 10 is likely to overheat, and a structure capable of cooling from the lower side can be appropriately formed as described above. Therefore, the pump chamber 10 can be efficiently cooled, the pump performance can be improved, and the life of the functional component can be extended as described above, which is a special advantageous effect.

Further, in this embodiment, as shown in FIGS. 13 to 19, the cooling gap 60 between the pump chamber body portion 110 and the bearing body portion 120 is one end wall portion 10b and one end wall thereof. A plurality of columnar portions 115 are integrated with one structural wall portion 121a provided with a first bearing portion 40a facing the portion 10b, and the columnar portion 115 is provided. The cooling gap 60 is provided so as to be formed in the portion not provided. For example, when such a shape is manufactured by casting, the core may form a cooling gap 60. Further, the present invention is not limited to this, and as shown in FIG. 22, a member on the pump chamber body portion 110 side including one end wall portion 10b and a bearing facing the one end wall portion 10b. The member on the bearing body portion 120 side constituting the structural wall portion 121 of the portion 40 is composed of a separate member and is connected by the columnar connecting portions 111 and 122 formed on both sides to form a cooling gap 60. Of course you can.

Further, in the package type rotary pump unit according to the present invention, in addition to the configuration described above, the pump chamber 10 is at least one of the one end wall portion 10b and the other end wall portion 10c. The pump chamber 10 is provided before the exhaust side opening 50 is opened at a position facing the portion where the gas is compressed, and the compression ratio of the gas is maximized by the claws of the two rotors 30A and 30B. The front stage vent 51 communicated to the outside of the pump chamber 10 and the claws of the two rotors 30A and 30B communicate with each other so as to exhaust the gas to the outside of the pump chamber 10 including the stage where the compression ratio of the gas is maximized compared to the previous stage. The subsequent stage exhaust port is an exhaust port 55 provided on the other end wall portion 10c, and the exhaust port 55 is communicated with the outside of the pump chamber 10 to compress the gas. The front vent 51 may be provided so as to be closed by the rotor at the stage of maximizing the gas.

According to this, it is possible to prevent the exhaust gas from flowing back, suppress overheating of the pump chamber 10, and improve the pump performance. The synergistic effect of the backflow prevention effect of the exhaust gas and the cooling effect of the above-mentioned coolant can more effectively prevent overheating of the pump chamber 10 and improve the pump performance.

By the way, in the present embodiment, the two rotors 30A and 30B are supported in a cantilevered state, but the present invention is not limited to this, and the two rotors 30A as disclosed in Patent Document 1 are not limited thereto. , 30B can also be effectively applied to a package type rotary pump unit having a configuration in which 30B is supported from both sides via two rotary shafts 20A and 20B. Further, it can be effectively applied to a package type rotary pump unit having exhaust ports on both one end wall portion and the other end wall portion of the pump chamber body portion as disclosed in Patent Document 1. Therefore, the exhaust section coolant flow path may be provided on the side of one end wall portion after balancing with the exhaust section coolant flow path provided on the side of the other end wall portion.

Further, in the present invention, for example, by adjusting and controlling the temperature of the coolant, it is possible to expand the range of use of the present invention corresponding to the use in cold regions, and heat exchange so as to circulate the coolant. Of course, it is possible to selectively adopt the auxiliary management method and configuration used in the liquid cooling system, such as the configuration in which the cooling liquid is cooled by using a container.

Although various examples of the present invention have been described above, the present invention is not limited to the examples of the present invention, and it goes without saying that many modifications can be made without departing from the spirit of the invention. That is.

1 Sealed housing 1a Housing frame part 1b Base part 1c Housing cover part 2 Rotating pump 3 Electric motor 3a Rotating shaft 3b Coupling 3c Safety cover 4 Cooling liquid supply source 4a Cooling liquid supply connection port 4b Cooling liquid supply piping 4c Cooling Liquid discharge pipe 4d Coolant discharge connection port 5 Liquid-cooled heat exchanger 5a Pipe for heat exchange 5b Coolant connection pipe 6 Blower 7 Blower fan 8 Switchboard 9 Blower for cooling electrical components 10 Pump room 10a Cylinder 10b One End wall part 10c The other end wall part 11 Cylinder case 12 Side plate 14 Intake connection port 15 Intake port 16 Intake introduction pipe connection port 17 Backflow prevention valve 20A Rotating shaft (drive side rotating shaft)
20B rotating shaft (driven side rotating shaft)
21A gear (drive side gear)
21B gear (driven gear)
25 Pump cover 25a Circulating air inlet 25b Circulating air outlet 30A Rotor (drive side rotor)
30B rotor (driven rotor)
31 1st muffler part 32 2nd muffler part 33 Vibration buffer piping 34 2nd muffler part exhaust introduction port 35 2nd muffler part exhaust discharge port 37 Suspended member 40 Bearing part 40a 1st bearing part 40b First 2 Bearing 41 Bearing 42 Oil seal 45 Gearbox 50 Exhaust side opening 51 Front vent 55 Exhaust port 56 Exhaust flow path 57 First muffler exhaust port 60 Cooling gap 61 First flow path forming part 61a Coolant flow path forming surface 61b Cooling liquid flow control part 61c Inner loop mating part 61d Outer loop mating part 61e Exhaust flow path forming surface 61f Exhaust passage forming wall 61g Loop frame-shaped mating part 62 Second flow path forming part 62a Exhaust Flow path forming surface 62b Extension flow path forming surface 62c Peripheral mating part 63 Third flow path forming part 63a Extension flow path forming surface 65 Sealing member 71 Bearing part Coolant flow path 71a Coolant inlet connection part 71b Bearing part Coolant outlet Connection 71c First connection pipe 72 Exhaust coolant flow path 72a Exhaust coolant inlet Connection 72b Coolant inlet 72c Exhaust port peripheral flow path 72d Exhaust coolant outlet Connection 72e Second connection pipe 73 Extension part Coolant flow path 73a Extension part Coolant inlet connection part 73b Extension part Coolant outlet connection part 81 Operation part 82 Electrical parts 83 Inverter device 90 Drain discharge connection port 91 Drain pan 92 Drain pipe 93 Drain pan for heat exchanger 94 For heat exchanger Drain piping 100 Pump body 110 Pump chamber body part 115 Columnar part 120 Bearing body part 121 Structural wall part 121a One structural wall part 121b The other structural wall part 200 Electric rotary pump 300 Vibration damping member

Claims (6)

A package-type rotary pump unit including a rotary pump that sucks and exhausts gas, an electric rotary pump that drives the rotary pump, and a closed housing that includes the electric rotary pump.
A liquid-cooled heat exchanger that is arranged inside the closed housing and is cooled by receiving a cooling liquid supply from a coolant supply source arranged outside the closed housing.
The internal air in the closed housing, which is arranged inside the closed housing and contains the heated air generated by heating the air around the rotary pump by the operation of the rotary pump, is cooled to the liquid-cooled heat exchanger. Equipped with a blower to send to
The liquid-cooled flow path from the coolant supply source is the liquid-cooled heat exchanger and the rotary pump so that the rotary pump is also cooled by the coolant from the coolant supply source that has cooled the liquid-cooled heat exchanger. A packaged rotary pump unit characterized by being connected in series. The rotary pump includes a bearing body portion, a pump chamber body portion, and a first muffler portion.
The liquid cooling flow path from the cooling liquid supply source is such that the cooling liquid from the cooling liquid supply source flows in the order of the liquid cooling heat exchanger, the bearing body portion, the pump chamber body portion, and the first muffler portion. The package type rotary pump unit according to claim 1, wherein the rotary pump unit is connected in series. The circulating air inlet portion, which is arranged inside the closed housing and is provided so as to cover the rotary pump and into which the internal air circulating inside the closed housing is introduced, and the internal air including the heated air. The package type rotary pump unit according to claim 1 or 2, further comprising a pump cover portion formed so as to be provided with a circulating air outlet portion through which the air is discharged. The liquid-cooled heat exchanger is connected to the side of the circulating air outlet portion, and the liquid-cooled heat exchanger is connected.
The blower is characterized in that it is connected to the liquid-cooled heat exchanger so as to suck the internal air and flow it from the circulating air inlet portion to the circulating air outlet portion to pass through the liquid-cooled heat exchanger. The package type rotary pump unit according to claim 3. The rotary pump is a biaxial rotary pump, one rotor rotary shaft is connected in series with the rotary shaft of the electric motor and is rotated, and the other rotor rotary shaft is connected to the one rotor rotary shaft via a gear. Is provided so as to rotate synchronously in the opposite direction, and is a space on the extension of the axis on which the other rotor rotation shaft is arranged, and the electric motor and the one rotor rotation shaft are connected to each other. The package-type rotary pump unit according to any one of claims 1 to 4, wherein the liquid-cooled heat exchanger and the blower are arranged in a space adjacent to the portion. The electric motor is provided with a blower fan for cooling the electric motor that blows air so as to cool the electric motor, and the blower fan is arranged on the side opposite to the side connected to the one rotor rotation shaft. The package type rotary pump unit according to claim 5, wherein the package type rotary pump unit is provided so as to blow air toward a motor main body.

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