JP7399495B2 - Packaged rotary pump unit - Google Patents

Description

The present invention relates to a package type rotary pump unit that includes an electric rotary pump that includes a rotary pump that sucks and exhausts gas, an electric motor that drives the rotary pump, and a sealed casing that encloses the electric rotary pump.

A conventional packaged rotary pump unit includes a pneumatic device such as a vacuum pump or blower that generates negative or positive air pressure, a storage box that houses a plurality of the pneumatic devices and provides soundproofing, and a storage box that is heated by the pneumatic device. A blower device that generates a cooling air flow flowing through the storage box in order to cool the inside of the storage box, and a cooling means such as a water-cooled cooler provided to allow the cooling air flow to pass through and cool the storage box. A pneumatic device station, characterized in that the air blower is provided above the position where each pneumatic device is placed so as to suck air from below and discharge it upward. (see Patent Document 1) has been proposed by the present applicant.

Furthermore, as an example of a rotary pump built into a package type rotary pump unit, as shown in FIG. The pump chamber includes a cylinder portion 10a, one end wall portion 10b provided on one end surface of the cylinder portion 10a, and another end wall portion 10c provided on the other end surface of the cylinder portion 10a. Two rotating shafts 20A, 20B are arranged in parallel within the pump chamber 10 and rotated at the same speed in opposite directions; two rotors 30A and 30B formed with hook-shaped claws so as to be able to compress and exhaust the gas sucked in by being rotated in a non-contact state; the one end wall portion 10b and the other end wall portion; 10c, the rotary pump (claw pump) is equipped with an exhaust side opening 50 that is opened at a position facing the part in the pump chamber 10 where the gas is compressed. The exhaust side opening 50 is a pre-stage vent 51 that communicates with the outside of the pump chamber 10 at a pre-stage where the gas compression ratio is maximized by the claws of the two rotors 30A and 30B. , a rear-stage exhaust port (exhaust port) that communicates with the claw portions of the two rotors 30A and 30B to exhaust the gas to the outside of the pump chamber 10, including a stage in which the compression ratio of the gas is maximized compared to the previous stage. 55), and at the stage where the latter stage exhaust port (exhaust port 55) is communicated with the outside of the pump chamber 10 and the compression ratio of the gas is maximized, the first stage ventilation port 51 is closed by the rotor 30A. and a pump chamber body section provided by a cylinder section 10a and end walls 10b and 10c provided on both end surfaces of the cylinder section, respectively, to form the pump chamber 10, and the two rotors. 30A, 30B are disposed at one end of the two rotating shafts 20A, 20B, respectively, and are provided with a bearing portion 40 that supports the two rotating shafts 20A, 20B in a cantilevered manner. 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 body and the pump body (see Patent Document 2).

According to the claw pump proposed by the present applicant, the exhaust side opening 50 is constituted by a front stage ventilation port 51 and a rear stage exhaust port (exhaust port 55) which are opened separately. For this reason, when used as a vacuum pump at a high degree of vacuum, for example, unsuperheated outside air is sucked into the pump chamber 10 at the front stage vent 51, and the exhaust gas flows backward at the rear stage exhaust port (exhaust port 55). By being able to prevent the pump chamber 10 from overheating, the pump performance can be improved.

Patent No. 5119558 (Claim 1, Figure 1) Patent No. 6749714 (Claim 1, Figure 3)

The problem that we are trying to solve regarding packaged rotary pump units is that in conventional packaged rotary pump units, cooling air is introduced from the outside and the air heated by the rotary pump is discharged to the outside of the housing. A structure has been proposed to reduce noise by enclosing the rotary pump, although it is incomplete, but in cases where the rotary pump is built in a sealed housing, the noise generated by the operation of the rotary pump can be reduced. The problem is that no consideration has been given to a means for further significantly reducing the sound, and a structure that can reduce the sound more rationally and effectively.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a packaged rotary pump unit that can more rationally and effectively reduce the noise generated by the operation of a rotary pump when the rotary pump is built in a sealed casing. It is in.

The present invention includes the following configuration to achieve the above object.
According to one embodiment of the packaged rotary pump unit according to the present invention, an electric rotary pump including a rotary pump that sucks and exhausts gas and an electric motor that drives the rotary pump, and a sealed casing that includes the electric rotary pump. A package-type rotary pump unit comprising: the rotary pump having a noise-reducing unit that also serves as an exhaust cooling unit in which the exhaust gas is cooled by a coolant supplied from a coolant supply source disposed outside the sealed casing; A first muffler section that produces an effect is provided, and a second muffler section that introduces and muffles the exhaust gas that has passed through the first muffler section is disposed above the electric rotary pump inside the sealed casing. has been done.

Moreover, according to one form of the package type rotary pump unit according to the present invention, the second muffler section is constituted by a plurality of sound reduction chambers, and the plurality of sound reduction chambers are configured to be connected to the rotary pump and the electric motor. It may be characterized in that they are arranged in series in the same direction as the connection direction of the sealed casing and in the longitudinal direction of the sealed casing.

Further, according to one embodiment of the packaged rotary pump unit according to the present invention, the second muffler section may be installed in a suspended state inside the sealed casing. can.

Moreover, according to one form of the package type rotary pump unit according to the present invention, the electric rotary pump is installed in the sealed casing via a vibration damping member, and the first muffler part and the second muffler part are connected to each other. The device may be characterized in that the parts are connected to each other via vibration damping piping.

Further, according to one embodiment of the packaged rotary pump unit according to the present invention, the second muffler section is arranged on the back side inside the sealed casing, and the power distribution board is arranged on the front side. can be characterized by

Further, according to one embodiment of the packaged rotary pump unit according to the present invention, the packaged rotary pump unit is arranged inside the sealed casing and receives the cooling liquid from a cooling liquid supply source arranged outside the sealed casing. A liquid-cooled heat exchanger to be cooled, and internal air in the sealed casing that is arranged inside the sealed casing and includes heated air generated when the air around the rotary pump is heated by operation of the rotary pump. , and a blower device that sends air to the liquid-cooled heat exchanger to cool it.

According to the packaged rotary pump unit of the present invention, when the rotary pump is built in a sealed casing, the noise generated by the operation of the rotary pump can be reduced more rationally and effectively. have a beneficial effect.

FIG. 2 is a block diagram schematically showing a liquid cooling flow and a circulating gas (air) flow inside a sealed casing in an embodiment of a packaged rotary pump unit according to the present invention. FIG. 2 is a block diagram schematically showing a liquid cooling flow and an exhaust flow of an example of the package type rotary pump unit according to the present invention. FIG. 2 is a perspective view showing the inside of a sealed casing, which is an example of the package type rotary pump unit according to the present invention. FIG. 4 is a perspective view showing a state in which the pump cover portion of the embodiment of FIG. 3 is removed. FIG. 4 is a plan view of an electric rotary pump installed in the embodiment of FIG. 3; FIG. 6 is a plan view showing a state in which the pump cover portion of the embodiment of FIG. 5 is removed. FIG. 4 is a rear view of the embodiment of FIG. 3; FIG. 2 is a perspective view showing the appearance of an example of a package type rotary pump unit according to the present invention in which two electric rotary pumps are housed in upper and lower stages. 9 is a perspective view showing the internal structure of the sealed casing of the embodiment shown in FIG. 8. FIG. 9 is a side view showing the internal structure of the sealed casing of the embodiment shown in FIG. 8. FIG. FIG. 9 is a perspective view showing the internal structure of the sealed casing of the embodiment shown in FIG. 8 with the power distribution board removed. FIG. 9 is a front view showing the internal structure of the sealed casing of the embodiment shown in FIG. 8 with the power distribution board removed. FIG. 2 is a cross-sectional perspective view illustrating the internal structure of an example of the rotary pump (claw pump) mounted in the packaged rotary pump unit according to the present invention, broken in a stepwise manner. 14 is a front perspective view of the embodiment of FIG. 13. FIG. 14 is a rear perspective view of the embodiment of FIG. 13. FIG. FIG. 14 is a front view of the embodiment of FIG. 13; 14 is a rear view of the embodiment of FIG. 13. FIG. FIG. 14 is a plan view of the embodiment of FIG. 13; FIG. 14 is a cross-sectional perspective view showing a bearing coolant flow path in the embodiment of FIG. 13; FIG. 14 is an exploded view showing a coolant flow path forming surface that is the inner surface of the first flow path forming portion in the embodiment of FIG. 13; FIG. 2 is an exploded view showing an exhaust flow path forming surface which is an outer surface of a first flow path forming portion in the embodiment of FIG. 1; FIG. 1 is an exploded view showing a conventional rotary pump.

Hereinafter, an embodiment of a 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 based on the accompanying drawings (FIGS. 1 to 21). Note that the embodiment of the rotary pump according to the present invention is a vacuum pump, and is a water-cooled two-shaft rotary pump (claw pump). However, the rotary pump according to the present invention is not limited to this example, and includes pumps that can be used as blowers that use the discharged gas as product gas, and single-shaft rotary pumps such as vane pumps. This also includes those that use other liquids as cooling fluids.

The package type rotary pump unit according to the present invention includes, as a basic configuration, an electric rotary pump 200 that includes a rotary pump 2 that sucks and exhausts gas, and an electric motor 3 that drives the rotary pump 2, and the electric rotary pump 200. The device is equipped with a sealed casing 1.

Note that the sealed casing 1 according to the present invention does not need to be tightly sealed with a strict airtight seal, but must be such that gas (in this embodiment, air) can flow in and out between the inside of the casing and the outside world. The enclosure may be any enclosure that forms a closed space that is restricted to That's fine. That is, in the sealed casing 1 according to the present invention, a slight gap is allowed, and structural members such as steel plates constituting the casing are brought into contact with each other without using a sealing material as in this embodiment. The degree of sealing may be sufficient to sufficiently restrict air circulation.

The sealed casing 1 of this embodiment has a rectangular box shape, and includes a casing frame portion 1a (see FIGS. 3, 9, etc.), a base portion 1b (see FIGS. 3, 9, etc.), and a casing cover. A portion 1c (see FIG. 8) is provided. The sealed casing 1 has a skeletal structure in which a casing frame portion 1a made of square steel pipes, angle steel, or the like is covered by a casing cover portion 1c made of a steel plate or the like.
Inside this sealed casing 1, an electric rotary pump 200 including a rotary pump 2 and an electric motor 3, a liquid-cooled heat exchanger 5, an air blower 6, a pump cover part 25, a switchboard 8, a first muffler part 31, a first 2, a blower 9 for cooling electrical components, a drain pan 91, various types of piping, various types of electrical wiring, and their accessories are arranged.

Reference numeral 5 denotes a liquid-cooled heat exchanger, which is arranged inside the sealed casing 1 and receives cooling liquid from a cooling liquid supply source 4 arranged outside the sealed casing 1, as shown in FIGS. 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. Note that 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 heat exchanger in which a heat exchange pipe 5a through which a cooling liquid passes is housed in a reciprocating state (zigzag) in a rectangular box-shaped heat exchange chamber. It is provided in the form of In the rectangular box-shaped heat exchange chamber of this embodiment, the rectangular inlet on which internal air (circulating air) is introduced is connected to the circulating air outlet section 25b of the pump cover section 25, which will be described later. A rectangular discharge port from which internal air (circulated air) is discharged is connected to a blower device 6, which will be described later. This constitutes a fan cooler having a liquid-cooled heat exchanger 5. Note that the liquid-cooled heat exchanger 5 is of a general form, so detailed illustration thereof will be omitted. Furthermore, it goes without saying that in the liquid-cooled heat exchanger 5, the form of the flow path for the cooling liquid and the form of the path for the circulating air cooled by heat exchange can be selectively set as appropriate.

Here, the coolant supply source 4 can be a liquid cooling device that cools liquid using a refrigeration cycle. Note that depending on the location conditions, other cooling sources such as air (outside air), fresh water, seawater, ice, and groundwater may be used, and it is of course possible to use a combination of multiple cooling sources as appropriate. It is. Note that the cooling liquid in this embodiment is cooling water, and is supplied from the same cooling liquid supply source 4 that cools the exhaust gas discharged from the exhaust port 55, as described later.

Reference numeral 6 denotes a blower, which is disposed inside the sealed casing 1 and contains heated air generated when the air around the rotary pump 2 is heated by the operation of the rotary pump 2. It is provided as a means for sending internal air to the liquid-cooled heat exchanger 5 for cooling. Note that in FIG. 1, the flow of internal air is schematically shown by thick arrows.
The blower device 6 of this embodiment is an axial fan, and is arranged along the longitudinal direction of the electric rotary pump 200 so as to suck in and discharge internal air. Note that the blowing device 6 is not limited to an axial fan, and it goes without saying that other blowing means such as a centrifugal fan (for example, a sirocco fan) may be selectively used as appropriate.

According to the packaged rotary pump unit according to the present invention, the amount of heat generated is generated when the rotary pump unit 2 is operated in a high-temperature environment or when the rotary pump 2 housed in the sealed housing 1 is used as a vacuum pump, for example, in a range with a high degree of vacuum. Even if the pump is large, the air inside the sealed casing 1 can be prevented from being overheated, which has the particularly advantageous effect of maintaining high pump performance and extending the life of the device. That is, by causing the internal air in the sealed housing 1 to flow through the air blower 6 and passing through the liquid-cooled heat exchanger 5, overheated air is prevented from stagnation around the rotary pump 2, and the internal air is efficiently used. Can be cooled by good circulation. Therefore, it is possible to appropriately suppress the temperature rise inside the sealed casing 1 caused by the heat generated by the rotary pump 2, etc., and to prevent adverse effects on the electric motor 3 and electrical components, etc., so that high pump performance can be maintained and the device lifespan can be maintained. can be extended over a long period of time.

In addition, all or most of the waste heat to the outside of the sealed housing 1 is mediated by the cooling liquid (cooling water) for heat exchange, so the heat radiation to the surroundings can be minimized and the installation environment It has the advantage that the impact is extremely small. For example, it is possible to reduce the burden of air conditioning in a room in which the packaged rotary pump unit according to the present invention is installed.
Furthermore, since the sealed housing 1 provides a sealed structure, there is also the advantage that the effect of reducing operating noise is large. In addition, according to the example of the sealed structure using the sealed casing 1 according to this embodiment, the noise can be reduced to 73 dB.
By creating a sealed structure with the sealed housing 1, the flow of gas between the inside of the housing and the outside world is sufficiently restricted, so even in high humidity environments, condensation inside the housing can be prevented. generation amount is small. That is, if the cooling liquid can be supplied, the internal temperature of the sealed casing 1 will be less affected by the product installation environment (temperature and humidity), so it can be used in a wide range of environmental temperature and humidity.
Note that, as will be described later, in this embodiment, the first muffler section 31 and the second muffler section 32 are housed in the sealed casing 1, and including the heat dissipated from these muffler sections, It is configured so that the air inside the sealed housing 1 can be cooled.

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

According to this pump cover part 25, the heat generated by the rotary pump 2 can be kept inside the pump cover part 25, and the heat is radiated to the outside of the pump cover part 25, and the entire inside of the sealed casing 1 is heated. Dispersion into space can be suppressed. According to this, by not dispersing the heat generated by the rotary pump 2, high-temperature air (heated air) can be sent to the liquid-cooled heat exchanger 5 in a collected state, 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, heat exchange can be performed efficiently, and the temperature rise in the sealed casing 1 can be efficiently suppressed. In addition, since the high-temperature air is sent to the liquid-cooled heat exchanger 5 in a collected state, the circulating air outlet section 25b has a constricted flow path, which allows the liquid-cooled heat exchanger 5 to be made smaller and reduce product costs. It also reduces

The pump cover part 25 of this embodiment is configured to exhaust the rotary pump 2 so that the internal air can effectively cool the entire outer surface of the rotary pump 2 by flowing so as to effectively contact the entire outer surface of the rotary pump 2. A circulating air inlet portion 25a that surrounds the rotary pump 2 and is open in the shape of a band is formed on the side (the side opposite to the side to which the electric motor 3 is connected). The circulating air outlet section 25b from which internal air including heated air heated by the rotary pump 2 is discharged has a narrowed flow path so as to collect the internal air and guide 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 inlet in the heat exchange chamber of the liquid-cooled heat exchanger 5 in an airtight seal state. According to this, the flow of internal air can be appropriately generated, the internal air can be appropriately circulated, heat exchange can be performed efficiently, and the temperature rise in the sealed casing 1 can be efficiently suppressed.

Further, in this embodiment, the inlet of the liquid-cooled heat exchanger 5 is connected to the circulating air outlet section 25b, and the blower device 6 sucks the internal air from the circulating air inlet section 25a to the circulating air outlet section. 25b and is connected to the liquid-cooled heat exchanger 5 so as to pass through the liquid-cooled heat exchanger 5. In this embodiment, the internal air suction port of the blower device 6 is connected to the internal air discharge port in the heat exchange chamber of the liquid-cooled heat exchanger 5 in an airtight manner.

According to this, a smooth flow of internal air can be generated rationally and effectively, the internal air can be circulated efficiently, heat exchange can be performed efficiently, and the temperature inside the sealed housing 1 can be Increase can be effectively suppressed. In addition, since the blower device 6 is disposed on the liquid-cooled heat exchanger 5 as in this embodiment, the blower device 6 itself sucks the air cooled by the liquid-cooled heat exchanger 5, resulting in overheating. This prevents damage and prolongs the life of the device.
In this embodiment, the pump cover section 25 (see FIGS. 3 to 6, etc.) is provided to cover the range of the pump chamber body section 110 and the bearing body section 120 (see FIGS. 13 to 18, etc.) of the rotary pump 2. It is being That is, as will be described later, it effectively covers areas with high surface temperatures, excluding the first muffler part 31 which is liquid-cooled. In addition, the size of the gap (width of the ventilation path) provided between the inner surface of the pump cover section 25 and the outer surface of the rotary pump 2 is determined so that the circulating air inlet section 25a is appropriately formed. It is sufficient that the airflow resistance during flow is not increased as much as possible, and the internal air heated by the heat generated by the rotary pump 2 (heated air) 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 two-shaft rotary pump, in which one rotor rotation shaft (rotation shaft 20A) is connected in series to the rotation shaft 3a of the electric motor 3 and rotated, and the other rotor rotation shaft A shaft (rotary shaft 20B) is provided to be rotated synchronously with one rotor rotary shaft (rotary shaft 20A) in the opposite direction via a gear, and the other rotor rotary shaft (rotary shaft 20B) is arranged. A liquid-cooled heat exchanger 5 and an air blower are installed in a space that is an extension of the axial center of the rotating shaft 20B and is adjacent to a portion where the electric motor 3 and one of the rotor rotating shafts (rotating shaft 20A) are connected. 6 is placed.

According to this, the internal space of the sealed casing 1 can be suitably utilized, and the internal air can be suitably circulated.
Note that one rotor rotating shaft (rotating shaft 20A) of this embodiment and the rotating shaft 3a of the electric motor 3 are connected in series via a coupling 3b, as shown in FIG. 4 and the like. Further, as shown in FIG. 3 and the like, 3c is a safety cover, which covers the connecting portion of the rotating shaft (3a, 20A) including the rotationally driven coupling 3b for safety. Furthermore, the coupling 3b may be configured to have a blower blade coaxially attached to the rotating shaft (3a, 20A) to blow air. According to this blower blade, cooling performance can be improved.

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

According to this, as shown by the thick arrow in FIG. Temperature rise can be efficiently suppressed. That is, as shown in FIG. 1, the internal air is first heated by passing through the inside of the pump cover part 25 by being sucked in by the blower 6, and then cooled by passing 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 (leftward from the blower device 6 in FIG. 5), and is discharged to the side of the electric motor 3 ( It flows above the electric motor 3 in FIG. Next, the internal air cooled by the liquid cooling heat exchanger 5 and discharged from the blower device 6 hits the inner surface of the sealed casing 1, and a portion of the internal air is sucked into the blower fan 7 of the electric motor 3. The water is reversed and flows to cool the motor body of the electric motor 3, and then flows toward the body of the rotary pump 2. Then, the internal air that has flowed around the pump cover section 25 is reversed and drawn into the inside of the pump cover section 25 through the circulating air inlet section 25a by the suction force of the blower device 6. As described above, by generating the air flow, the internal air can be appropriately circulated, heat exchange can be performed efficiently, and the temperature rise within the sealed casing 1 can be efficiently suppressed.

Furthermore, in this embodiment, the air in the switchboard 8 formed in the shape of a small chamber is circulated through the switchboard 8 formed on the front side of the sealed housing 1, as shown in FIGS. 1, 9, and 10. As an air cooling means, a blower 9 for cooling electrical components is installed at the bottom 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 casing 1 is sucked into the switchboard 8, and the air is drawn from the bottom to the top within the switchboard 8. Air can be blown so as to flow and be discharged from an opening in the upper part of the switchboard 8 (not shown). As a result, electrical components 82, inverter devices 83, and the like that generate a lot of heat installed in the switchboard 8 can be efficiently cooled. Further, the internal air discharged from the switchboard 8 is sucked into the inside of the pump cover section 25 from the circulating air inlet section 25a of the pump cover section 25. Note that, as shown in FIGS. 9 and 10, reference numeral 81 is an operating section, and since it generates low heat, in this embodiment, an air cooling means is not provided individually, and it is arranged at a position away from the switchboard 8.

Further, in this embodiment, as will be described in detail based on FIGS. 13 to 21, the rotary pump 2 is connected to the cooling liquid 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 cooling heat exchanger 5, and then cools the exhaust gas discharged from the exhaust port 55 (see FIG. 13, etc.). The pipes are connected in series. In this way, by liquid-cooling both the liquid-cooled heat exchanger 5 and the rotary pump 2, it is possible to effectively suppress a rise in temperature within the sealed casing 1.

Next, specific examples of the flow path for the coolant supplied from the coolant supply source 4 will be described based on the drawings (FIGS. 1, 3, 7, 9 to 15, etc.).
The coolant supply source 4 is connected to a coolant supply connection port 4a provided on the back surface of the sealed housing 1, and the coolant is supplied from the coolant supply connection port 4a by a liquid flow pump (not shown). It passes through the supply pipe 4b and is first supplied to the liquid-cooled heat exchanger 5 to cool the liquid-cooled heat exchanger 5. In addition, in the embodiment shown in FIGS. 9 to 12 in which the electric rotary pumps 200 are arranged in two stages, the coolant supply pipe 4b is branched into two, and the coolant is supplied to each of the two stages of the electric rotary pumps 200. The two coolant discharge pipes 4c are connected to each other and the coolant is discharged.

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

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

The liquid-cooled heat exchanger 5 and the rotary pump 2 can be cooled by flowing through the above channels, and the coolant that has cooled the internal air of the sealed casing 1 and the lubricating oil and exhaust gas of the rotary pump 2 In this embodiment, the coolant is returned to the coolant supply source 4 and circulated. Note that when using underground water, it is of course possible to flow it in one direction without circulating it.

According to this, the liquid-cooled heat exchanger 5, the bearing part 40 of the rotary pump 2, the gear box 45, Three locations of the first muffler section 31, which is the exhaust section of the rotary pump 2, can be rationally cooled in order. In other words, regarding the temperature of each part, the allowable temperature of the oil stored in the gear box is higher than the allowable temperature of the air inside the sealed housing 1, and Since the temperature relationship is such that the permissible exhaust temperature of the rotary pump is even higher, it is reasonable to flow the cooling liquid in the above order. In other words, when sequentially cooling the three locations mentioned above, the cooling fluid is gradually heated, but each location has a temperature difference (temperature difference between the cooling fluid temperature and the temperature of the cooled part) that is sufficient to cool the area. can be maintained. Such liquid cooling piping connected in series has the advantage of simplifying the piping configuration and reducing costs.
Note that the liquid cooling pipes are not limited to this embodiment, and may be provided in parallel. By arranging the pipes in parallel, the flow rate can be adjusted individually, which has the advantage of allowing precise cooling control.

Next, specific measurement data (verification values) regarding the cooling effect inside the sealed casing 1 of the embodiments shown in FIGS. 1 to 7 will be explained.
Data was obtained by setting the temperature of the cooling liquid (cooling water) to 32° C. as an example of the highest expected temperature condition, 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 installed as in the embodiments shown in FIGS. 13 to 21 and water-cooled, the internal air of the sealed housing 1 is The temperature 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 this embodiment, the circulating air outlet section 25b of the pump cover section 25 The temperature of the internal air was 55°C, and the temperature of the internal air that passed through the liquid-cooled heat exchanger 5, was discharged from the blower 6, and was circulated to the electric motor 3 and the switchboard 8 was 45°C. As a result, the heat resistance temperature of the electric motor 3, electrical components 82, etc. could be sufficiently cleared. Further, the temperature of the cooling water returned to the cooling liquid supply source 4 became 40 to 45°C.

Incidentally, the intake piping of the rotary pump 2 is configured such that the intake introduction pipe connection port 16 can be connected to an external intake pipe, and outside air can be taken in through the external intake pipe. has been done. Further, a check valve 17 is connected between the intake intake pipe connection port 16 and the intake port 15 of the rotary pump 2, and is configured to regulate the flow of gas from the pump 2 to the intake intake pipe connection port 16. It is provided.
Further, 90 is a drain discharge connection port, which serves as a discharge port through which drain can be discharged to the outside. A drain pan 91 placed under the rotary pump 2 and a heat exchanger drain pan 93 placed on the liquid-cooled heat exchanger 5 are connected to this drain discharge connection port 90 through a drain pipe 92 and a heat exchanger drain pipe 94. It is possible to receive and properly discharge the generated drainage.

Next, the noise reduction structure of the packaged rotary pump unit according to the present invention will be explained in detail based on the accompanying 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 that includes a rotary pump 2 that sucks and exhausts gas, an electric motor 3 that drives the rotary pump 2, and an electric rotary pump 200 that rotates the The pump 200 includes a sealed casing 1 that encloses a pump 200.

The rotary pump 2 installed in the packaged rotary pump unit according to the present invention has an exhaust cooling section in which the exhaust gas is cooled by a coolant supplied from a coolant supply source 4 arranged outside the sealed housing 1. A first muffler section 31 is provided which also serves as a silencing effect. A second muffler section 32 that introduces the exhaust gas that has passed through the first muffler section 31 and muffles it is arranged above the electric rotary pump 200 inside the sealed casing 1 .

According to the package type rotary pump unit according to the present invention, when the rotary pump 2 is built in the sealed housing 1, the noise generated by the operation of the rotary pump 2 can be more rationally and effectively reduced. It has the particularly advantageous effect of being able to That is, the electric rotary pump 200 and the muffler ( The entire first muffler section 31 and second muffler section 32) can be effectively covered with the above-mentioned sealed case (sealed case 1). Therefore, the noise, including the sound leaking from the muffler, intermediate pipes, etc., can be shielded and absorbed, and the silencing effect can be effectively enhanced. The second muffler section 32 itself arranged above the electric rotary pump 200 also has the effect of shielding noise generated from the electric rotary pump 200. According to the example of the packaged rotary pump unit according to this embodiment, the noise can be reduced to 73 dB, and high quietness can be achieved. Further, by arranging the second muffler section 32 above the electric rotary pump 200, the foot space can be reduced. In order to improve the sound absorption performance, it goes without saying that a sound absorbing material may be attached to the inner surface of the member constituting the sealed casing 1.

In addition, in this embodiment, the second muffler section 32 is constituted by a plurality of sound reduction chambers, and the plurality of sound reduction chambers are arranged in the same direction as the connection direction of the rotary pump 2 and the electric motor 3, and are arranged in a sealed casing. They are arranged in series in the longitudinal direction of the body 1.

According to this, a plurality of sound reduction rooms 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 has a configuration in which the rotary pump 2 and the electric motor 3 are connected in series, it has a horizontally long shape, and the sealed casing 1 is also horizontally long as in this embodiment. It is formed. The second muffler section 32 can be appropriately disposed inside the horizontally long sealed casing 1 in accordance with the form of the electric rotary pump 200, and the overall configuration can be provided compactly. .

Note that the internal structure of the second muffler section 32 can be selectively designed to enhance the sound reduction (muffling) effect through expansion, shielding, sound absorption, etc. For example, by using three sound reduction chambers and arranging the three chambers in series, a compact structure with high sound reduction performance can be achieved.
More specifically, for example, in this embodiment, the second muffler section 32 has a cylindrical outer shape that is elongated in the axial direction. and a sound reduction chamber on the other end side. The sound is reduced by discharging the pipe so that it expands from the perforated part at the tip of the pipe. A pipe is connected 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 air is discharged to the sound reduction chamber on the other end side, thereby reducing noise by expansion. let Furthermore, in order to reverse the exhaust gas introduced into the sound reduction chamber at the other end, the The muffler is provided so that the exhaust gas is discharged to the sound reduction chamber in the middle part to reduce the sound by expansion, and the exhaust gas is discharged from the sound reduction chamber in the middle part to the outside via the exhaust outlet 35 of the second muffler part. It is being

Further, in this embodiment, the second muffler section 32 is installed in a suspended state inside the sealed casing 1. That is, as shown in FIGS. 3 and 9, the cylindrical second muffler section 32 of this embodiment is fixed to the upper part of the housing frame section 1a and is a hanging member extending downward. 37, and is installed in a suspended state from the upper part of the sealed casing 1.

According to this, by utilizing the space above the electric rotary pump 200, the muffler (second muffler section 32) has an appropriate volume with a high noise reduction effect due to expansion, and is lighter than other constituent devices. can be appropriately and easily arranged. Note that, of course, by appropriately attaching a sound absorbing material to the inner surface of each of the above-mentioned sound attenuation chambers of the second muffler section 32, it is possible to obtain a sound deadening effect through sound absorption.

Further, in this embodiment, as shown in FIGS. 3, 4, 7, and 9 to 12, the electric rotary pump 200 is installed in the sealed casing 1 via a vibration damping member 300, and the first The muffler section 31 and the second muffler section 32 are connected via a vibration damping pipe 33. That is, in this embodiment, the electric rotary pump 200 is installed on the base part 1b in the sealed casing 1 via the vibration damping member 300 provided with anti-vibration rubber, and is connected to the exhaust port 57 of the first muffler part and the second muffler part. A vibration damping pipe 33 is connected between the exhaust gas inlet 34 of the muffler section and the exhaust gas flows from the first muffler section 31 to the second muffler section 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 part 32 by the vibration buffer piping 33, the vibration of the electric rotary pump 200 is It is possible to reduce the amount of vibration being transmitted to the side of the housing 1, and it is possible to suitably obtain vibration-proofing and sound-proofing effects. Further, since the transmission of the vibrations of the electric rotary pump 200 to the second muffler section 32 can be reduced, the second muffler section 32 can be appropriately and more easily installed inside the sealed casing 1.

Further, in this embodiment, as shown in the package type rotary pump unit in which the electric rotary pump 200 is mounted in multiple stages (two stages in this embodiment) described in FIGS. 8 to 12, the second muffler section 32 is It is arranged on the back side of the inside of the sealed casing 1, and the power distribution board 8 is arranged on the front side. According to this, the switchboard 8 becomes a shielding part, and the noise transmitted to the front side can be further reduced. This further improves the working environment.

Next, as an example of a rotary pump used in the packaged rotary pump unit according to the present invention, an example of a claw pump will be described based on FIGS. 13 to 21.
In this claw pump, as shown in FIG. 13 etc., 110 is a pump chamber body part, and the cylinder is designed to form a pump chamber 10 (see FIG. 22) having a cross-sectional shape in which two circles are overlapped. 10a, one end wall 10b provided on one end surface of the cylinder portion 10a, and the other end wall 10c provided on the other end surface of the cylinder portion 10a.

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

Further, two rotors 30A and 30B are provided corresponding to the two rotating shafts 20A and 20B and arranged in the pump chamber 10, and are rotated in a non-contact state to compress and exhaust the inhaled gas. A hook-shaped claw portion (see FIG. 22) is formed and provided. 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 gas is discharged to at least the other end wall portion 10c of the pump chamber body portion 110. An exhaust port 55 is provided. This constitutes a packaged rotary pump unit, which is a type of two-shaft rotary pump.

In this embodiment, the two rotary shafts 20A, 30B are disposed corresponding to one end (one tip) of each of the two rotary shafts 20A, 20B, and supported in a cantilevered state. 20B is supported by the bearing part 40, one end wall part 10b of the pump chamber body part 110 is located on the side of the bearing part 40, and the other end wall part 10c of the pump chamber body part 110 has an exhaust port for discharging gas. 55 are provided. Note that 15 is an intake port, which is opened and provided at a position facing a portion of the pump chamber 10 where gas is not compressed. The intake port 15 of this embodiment is provided in the upper corner of the pump chamber body part 110, and is cut out across the upper wall part of the cylinder part 10a and the upper part of one end wall part 10b. It is being Reference numeral 14 denotes an air intake connection port, which is connected at its lower end to the air intake port 15 and at its upper end to a pneumatic device (not shown) via a conduit.

In the package type rotary pump unit according to the present invention, an exhaust gas 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. A cooling liquid flow path 72 is provided. In addition, in this embodiment (example when used as a vacuum pump), the state in which exhaust gas is discharged from the exhaust port 55 means that the pump chamber 10 is open and communicated with the atmosphere (air) that is outside air. The exhaust gas will be released into the atmosphere (air). In addition, the coolant liquid is typically coolant water, but it also includes mixed liquids with water (aqueous solutions) such as antifreeze, oil, etc., and of course other liquids other than water can also be used. be.

According to the packaged rotary pump unit according to the present invention, even when the vacuum pump is used in a high vacuum range where the ultimate vacuum is closer to absolute vacuum, the pump chamber 10 can be prevented from being overheated. This can be prevented more actively and effectively, and pump performance can be significantly improved.

That is, by providing the exhaust coolant flow path 72 on the side of the other end wall portion 10c of the pump chamber body portion 110, the exhaust gas immediately after being discharged from the exhaust port 55 can be effectively cooled by the coolant. can. According to this, even if the vacuum pump is used in a high degree of vacuum range above a certain level and is heated due to backflow of exhaust gas, an increase in the internal temperature of the pump chamber 10 can be suppressed. Therefore, it is possible to set a small clearance between the inner wall surface of the pump chamber 10 and the two rotors 30A and 30B so that they do not come into contact with each other, and gas leakage due to this clearance can be reduced, thereby improving pump efficiency. You can improve.

Furthermore, according to the packaged rotary pump unit according to the present invention, by setting the clearance small as described above, it is possible to further increase the ultimate degree of vacuum, and even if there is a backflow of exhaust gas, overheating can be prevented, so that the The opening area of the port 55 can be set wider, and a vacuum pump with a larger processing air volume can be constructed.

According to the packaged rotary pump unit of this embodiment, the side of the other end wall 10c where the exhaust port 55, which is heated the most, is provided is locally actively cooled. There is. That is, in order to reduce the temperature difference in the pump chamber body section 110 where a large temperature gradient (temperature difference) occurs, the other wall section of the pump chamber body section 110 centered on the exhaust port 55 is The configuration is such that the exhaust gas is cooled by preferentially cooling the side 10c. By cooling the exhaust air in this way and preventing overheating of the pump chamber 10, it has been confirmed in the example that the internal temperature difference is reduced by about 140 degrees Celsius, and the ultimate vacuum level is increased to 97 kPa. This allows the pump performance to be significantly improved. Conventionally, the limit for continuous operation is that the ultimate vacuum level is approximately 90 kPa in order to avoid contact (internal interference) between the wall surface of the pump chamber 10 and the two rotors 30A and 30B. All I could do was drive. In contrast, according to the present invention, shut-off operation with a higher degree of vacuum can be performed continuously.

By the way, in a package type rotary pump unit, the compressibility of the gas is high and the gas is heated and exhausted, so the exhaust port 55 is most likely to be overheated, and the other end wall portion where the exhaust port 55 is formed is most likely to be overheated. The part 10c becomes hotter than the other parts. The other portions of the pump chamber body portion 110 have a lower temperature than the other end wall portion 10c. For this reason, if the entire pump chamber body part 110 including the cylinder part 10a is cooled in the same way, the temperature difference between the exhaust port 55 of the other end wall part 10c and other parts will be maintained. Therefore, the problem of interference between the rotors 30A and 30B, which are operating parts, due to thermal expansion cannot be solved.

Further, according to this embodiment, the coolant inlet 72b (see FIG. 20) for introducing the coolant into the exhaust section coolant flow path 72 is provided near the exhaust port 55, and the exhaust section coolant flow path 72 is provided near the exhaust port 55. A coolant flow regulating portion 61b is provided at the formed portion to regulate the flow of the introduced coolant so that the coolant circulates in the vicinity of the exhaust port 55 first. Note that, as shown in FIG. 20, the coolant flow regulating portion 61b of this embodiment is arranged at a plurality of locations (two locations in this embodiment) on a coolant flow path forming surface 61a of a first flow path forming portion 61, which will be described later. It is provided in the form of a rib-like protrusion.

According to this, by cooling the area around the exhaust port 55 (around the exhaust port 55) which is the most heated part of the pump chamber body part 110, the exhaust air immediately after the exhaust port can be effectively cooled. By lowering the temperature of the area around the exhaust port 55 and the exhaust gas, it is possible to prevent the area around the exhaust port 55 from being excessively heated and unevenly deformed due to thermal expansion in a well-balanced manner. In this way, the thermal expansion of the pump chamber body part 110 and the two rotors 30A and 30B can be suppressed in a well-balanced manner, so that the mutual clearance between them can be reduced, and the pump efficiency can be improved.

In addition, in a packaged rotary pump unit, from the viewpoint of drive stability, the exhaust port 55 is generally provided at a portion corresponding to the lower part of the pump chamber 10 (in this embodiment, the lower part of the other end wall 10c). become. In this embodiment, the coolant inlet 72b is disposed 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 expanded. The cooling liquid is first cooled with a low temperature cooling liquid, and the cooling liquid that has thus cooled the other end wall portion 10c is discharged upward through the exhaust cooling liquid outlet connection portion 72d. At this time, the cooling liquid undergoes heat exchange and its temperature rises, thereby decreasing its specific gravity and creating an upward flow vector. According to this flow of the coolant, the part 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 changed. You can arrange them. Therefore, the cooling liquid can be passed through smoothly, and the cooling efficiency can be effectively increased.

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

Note that, as shown in FIGS. 13, 20, and 21, the first flow path forming section 61 of this embodiment is provided by a plate-shaped member having unevenness formed on both sides so that flow paths are formed. It is fixed to the outer surface of the other end wall portion 10c with bolts, and the mating portion is watertightly sealed by a seal member 65 to form an exhaust coolant flow path 72. The mating portion of this embodiment includes an inner loop mating portion 61c formed in a rectangular loop frame shape that surrounds the exhaust port 55 so as to extend the exhaust path of the exhaust port 55, and a peripheral edge of the other end wall portion 10c. and an outer loop matching portion 61d formed to abut in a loop frame shape. An exhaust coolant flow path 72 is formed between the inner loop matching portion 61c and the outer loop matching portion 61d, and is filled with the coolant. According to this configuration, the outer wall surface of the other end wall portion 10c is brought into full contact with the cooling liquid and can be efficiently cooled. Further, this structure has a form in which the layered exhaust coolant flow path 72 is stacked planarly on the outside of the outer end surface of the pump chamber body portion 110, resulting in a compact configuration.

In addition, in the first flow path forming portion 61 of this embodiment, a portion of the exhaust coolant flow path 72 is provided on the coolant flow path forming surface 61a, which is a surface facing the outer surface of the other end wall portion 10c. The passage forming wall constituting the coolant flow regulating part 61b is provided in a protruding form so that an exhaust port surrounding passage part 72c, which is a groove-like 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. A passage forming wall (coolant flow regulating portion 61b) is provided to appropriately bend and guide the exhaust section coolant flow path 72. Note that 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 this embodiment, the surface of the first flow path forming section 61 opposite to the coolant flow path forming surface 61a is configured such that the exhaust gas is cooled by the first flow path forming section 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 exhaust gas discharged from the exhaust port 55 passes.

According to this exhaust flow path 56, the superheated exhaust gas can be effectively cooled, and by lowering the temperature of the exhaust gas, the temperature inside the pump chamber 10 is lowered, and the pump chamber body part 110 forming the pump chamber 10 and Overheating and thermal expansion of the two rotors 30A and 30B can be suppressed in a well-balanced manner.
Further, this exhaust flow path 56 can appropriately regulate the flow direction of the exhaust gas, and is designed to promote cooling of the exhaust gas, and also serves as a muffler structure to reduce exhaust noise. It has become. That is, the first muffler section 31 is configured by the structure in which this exhaust flow path 56 is formed. Note that 57 is an exhaust port of the first muffler section, which is opened and provided in the upper wall of the first flow path forming section 61, and serves as an exhaust port of the exhaust flow path 56. The air is exhausted to the outside through an exhaust port 57 in the muffler section. As shown in FIG. 21, the exhaust port 57 of the first muffler section of this embodiment is provided in a shape in which the flow path is narrowed on the inside side, and is formed to enhance the noise reduction effect.

Further, according to this embodiment, the exhaust flow path 56 is a portion disposed 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 disposing the second flow path forming part 62 including the exhaust flow path forming surface 62a provided to form the exhaust flow path 56 with the outer surface of the first flow path forming part 61, It is provided. According to this, the exhaust flow path 56 can be configured effectively and rationally, and the exhaust gas 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. . Moreover, this structure has a form in which the layered exhaust flow passages 56 are stacked planarly on the outside of the outer end surface of the pump chamber body portion 110, resulting in a compact configuration.

Note that, as shown in FIG. 13 etc., the second flow path forming portion 62 of this embodiment has an exhaust flow path forming surface that is an inner surface (a surface that comes into contact with the outer surface side of the first flow path forming portion 61). 62a is provided as a flat plate-shaped member, and is fixed to the outer surface (exhaust flow path forming surface 61e) of the first flow path forming portion 61 with bolts. Furthermore, on the side of the outer surface (exhaust flow path forming surface 61e) of the first flow path forming part 61 with respect to this exhaust flow path forming surface 62a (flat surface), there is a groove-shaped groove that becomes the exhaust flow path 56. The exhaust passage forming wall 61f is provided in a protruding form so that a passage is formed. The loop frame-like mating portion 61g and the exhaust passage forming wall 61f on the outer circumferential side of the first flow path forming portion 61 and the inner surface of the second flow path forming portion 62 are substantially closely fixed together. It can be made airtight either directly or by arranging a sealing member to make it airtight. Note that 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. As shown in FIG. 21, the exhaust flow path 56 is formed into a complicatedly curved flow path, which not only promotes cooling of the exhaust gas but also functions appropriately as a muffler chamber to further reduce exhaust noise. can be reduced.

Further, according to the present embodiment, the extension coolant flow path 73 that is continuous with the exhaust coolant flow path 72 is connected to the second flow path forming portion 62 on the outer surface of the second flow path forming portion 62 ( A portion disposed so as to cover the side of the extended flow path forming surface 62b), and between the outer surface (extended flow path forming surface 62b) of the second flow path forming portion 62, the extended portion cooling liquid flow path A third flow path forming portion 63 including an extended flow path forming surface 63a provided to form a channel 73 is provided. According to this, the extension coolant flow path 73 can be configured effectively and rationally. Moreover, this structure has a form in which the layered extension coolant flow passages 73 are stacked planarly on the outside of the outer end surface of the pump chamber body part 110, resulting in a compact structure. Furthermore, noise can be reduced by this layered extension coolant flow path 73 and the structural wall that constitutes it. That is, the structure forming this extension part coolant flow path 73 and the above-mentioned exhaust part coolant flow path 72 is a structure that blocks sound and reduces noise, and is a component of the first muffler part 31. It has also become

Note that, as shown in FIG. 13 etc., the third flow path forming portion 63 of this embodiment is provided by a flat plate-like member (plate member), and is connected to the second flow path forming portion 62 by bolts. , and is watertightly sealed by a sealing member 65 to a peripheral edge matching portion 62c provided in a loop frame shape on the outer surface of the second flow path forming portion 62, so that an extension coolant flow path 73 is formed. It is set in. In addition, in this embodiment, the extension coolant flow path 73 has a shape in which the coolant is retained in a flat layered space, but the present invention is not limited to this, and any suitable shape may be used. Of course, it is also possible to set the flow path in the flow path. Furthermore, it is also possible to increase the cooling performance by making the extension coolant flow path 73 multi-layered. In addition, in this extension coolant flow path 73 as well, similarly to the exhaust coolant flow path 72, the coolant is connected to the top of the second connection pipe 72e so that the coolant flows from the bottom to the top. A second connection is made from the exhaust coolant outlet connection part 72d provided and connected to the exhaust coolant flow path 72 to the extension coolant inlet connection part 73a provided at the lower part of the second connection pipe 72e. An extension coolant outlet connection part 73b is provided at the top so that the coolant that has flowed through the extension coolant flow path 73 through the pipe 72e is discharged to the outside.

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

Next, an example of the configuration of the two-shaft rotary pump according to the present invention, which cools the bearing portion 40 that supports the two rotating shafts 20A and 20B, will be explained in detail based on the accompanying drawings (FIGS. 13 to 21). do. The two-shaft rotary pump of this embodiment is a packaged rotary pump unit as explained above, but the present invention is not limited to this, and can be applied to other two-shaft rotary pumps such as roots pumps and screw pumps. It can also be applied to pumps. In addition, the two-shaft rotary pump according to the present invention is not limited to the configuration in which the two rotors 30A and 30B are cantilevered and supported as in the present embodiment, and the rotary shafts 20A and 20B are rotated at both ends. The structure can also be applied to a two-shaft rotary pump with freely bearing bearings.

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

The pump body 100 is arranged between the pump chamber body section 110 and the bearing body section 120 so that a cooling gap 60 that can suppress heat conduction is formed between the pump chamber body section 110 and the bearing body section 120. A bearing cooling section for passing cooling fluid is provided in a structural wall section 121 (in this embodiment, one structural wall section 121a) located on the pump chamber body section 110 side of the bearing body section 120. A liquid flow path 71 is provided.

According to this, the cooling liquid passing through the bearing cooling liquid flow path 71 has a heat transfer prevention effect of reducing the transfer of the heat of the compressed gas (exhaust gas) generated by the driving of the two rotors 30A and 30B to the bearing body part 120. The cooling effect has a particularly advantageous effect of extending the life of the functional parts constituting the bearing portion 40 and the like. That is, according to the present invention, by partitioning the pump chamber body part 110 and the bearing body part 120 and providing the cooling gap 60, heat conduction can be suppressed so that the amount of heat transfer is minimized, and the bearing part Since the bearing body portion 120 can be more actively cooled by the cooling fluid passing through the cooling fluid flow path 71, the reliability of the device can be improved. In this example, it has been confirmed that the temperature rise of the lubricating oil can be reduced by about 40°C.
Note that the functional parts are constituent members including the bearing 41 and the oil seal 42, and are treated as consumable parts. Running costs can be reduced by extending the lifespan of these functional parts.

By the way, the bearing part 40 of this embodiment has the pump chamber body part 110 in the bearing body part 120 so as to bear the two rotating shafts 20A, 20B between the two gears 21A, 21B and the two rotors 30A, 30B. A first bearing portion 40a provided on a side structural wall portion (one structural wall portion 121a), and a structural wall portion opposite to the first bearing portion 40a that is provided with a drive motor (electric motor 3 (FIG. 3)). etc.)) and a second bearing part 40b provided so as to bear the two rotating shafts 20A and 20B on the structural wall part (the other structural wall part 121b) arranged on the side to which the two rotating shafts 20A and 20B are connected. ing. Note that the rotating shaft 3a of the electric motor 3 is connected to a rotating shaft 20A (drive-side rotating shaft) via a coupling 3b (see FIG. 4, etc.).

In addition, in this embodiment, the two rotating shafts 20A and 20B are installed horizontally, and the bearing coolant flow path 71 is connected to the lubricating oil stored in the gear box 45. The lubricating oil 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 the stored state when the bearing body portion 120 is at rest. Note that the liquid level of the lubricating oil when it is at rest is set to be located between the inner bottom surface of the gear box 45 (oil chamber) and the rotating shafts 20A and 20B that are arranged horizontally. According to this, the lubricating oil can be effectively cooled, and by being scraped up by the two rotating gears 21A and 21B, the lubricating oil lubricates the gears 21A and 21B and the bearing 41, and also lubricates the inside of the gear box 45. can be cooled.

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

Furthermore, 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 coolant flow path 71 is provided at the lower part of the structural wall 121 of the bearing body 120 as described above, heat conduction is effectively suppressed, and the bearing 40 is Overheating can be suppressed.

In addition to the configuration provided in the horizontal type installed by horizontally arranging the two rotating shafts 20A and 20B as in this embodiment, the cooling gap 60 is A blower means for blowing air may be provided. According to this, the pump chamber body part 110 and the bearing body part 120 can be effectively air-cooled, and the reliability of the two-shaft rotary pump can be further improved. That is, since cooling air can be appropriately flowed between the pump chamber body part 110 and the bearing body part 120, heat transfer can be more effectively suppressed, and cooling by heat radiation can be promoted. Thereby, it is possible to suppress the temperature rise of the bearing body portion 120, and the life of the functional component can be extended.

According to the biaxial rotary pump of the present invention, the bearing coolant flow path 71 is provided in the pump chamber body 110 so that the coolant that has cooled the bearing body 120 cools the pump chamber body 110. The cooling liquid flow path may be connected to a coolant flow path. According to this, in order to prevent the lubricating oil from boiling and overheating, the temperature of the coolant flowing through the bearing coolant flow path 71 is higher than that of the coolant flowing through the coolant flow path provided in the pump chamber body portion 110. The temperature can be lowered than that of the flowing coolant, allowing effective use of the coolant.

Further, in this embodiment, the exhaust coolant flow path 72 is connected to the bearing coolant flow path 71 so that the coolant flows in the order from the bearing coolant flow path 71 to the exhaust coolant flow path 72. has been done. According to this, one cooling liquid supply source 4 (FIGS. 1 and 2) is used to connect structural walls 121 (one structural wall 121a) and the other end wall portion 10c side of the pump chamber body portion 110 can be effectively cooled directly and sequentially. Note that the coolant in this embodiment is supplied from the coolant supply source 4 (FIGS. 1 and 2), and is supplied from the coolant inlet connection portion 71a (FIGS. 15, 17, and 19) and the bearing coolant flow path 71. (Fig. 13, Fig. 19), the bearing coolant outlet connection part 71b (Fig. 14, Fig. 16, Fig. 18, Fig. 19), and then the first connection pipe 71c (Fig. 14, Fig. 16, Fig. 18). , FIG. 19), the exhaust coolant inlet connection 72a (FIGS. 14, 16, and 18), and the coolant inlet 72b (FIG. 20). ), flows through the extension coolant passage 73, and is discharged to the outside of the pump 2. However, the present invention is not limited to this, and it is of course possible to supply the coolant separately without connecting the bearing coolant flow path 71 and the exhaust coolant flow path 72, and to adjust the coolant supply individually. You may also try to optimize it by doing so.

In addition, in the flow path configured by the bearing coolant flow path 71, the exhaust coolant flow path 72, and the extension coolant flow path 73 of this embodiment, the exhaust portion is located above the bearing coolant flow path 71. A coolant flow path 72 is arranged, and the coolant flows from the bottom to the top in the exhaust coolant flow path 72 and the extension coolant flow path 73, and the direction of flow is determined by the temperature rise of the coolant. By aligning the flow direction of the cooling fluid and the flow direction of the cooling fluid, the cooling fluid can flow smoothly, and the bearing portion 40 and the exhaust gas can be effectively cooled.

According to the cooling structure of the biaxial rotary pump described above, the cooling performance can be improved in a rational manner in correspondence with 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 tends to overheat, and a structure that can be cooled from the lower side can be appropriately formed as described above. For this reason, the pump chamber 10 can be efficiently cooled, pump performance can be improved, and as mentioned above, a particularly advantageous effect can be achieved in that the lifespan of the functional parts can be extended.

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

Furthermore, in the package type rotary pump unit according to the present invention, in addition to the configuration described above, at least one of the end wall portions 10b and 10c, the pump chamber 10 The exhaust side opening 50, which is provided at a position facing the part where gas is compressed in the pump chamber 10, is located at the front stage where the compression ratio of the gas is maximized by the claws of the two rotors 30A and 30B. The front stage vent 51 communicates with 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 gas to the outside of the pump chamber 10, including a stage in which the compression ratio of gas is maximized compared to the front stage. The subsequent exhaust port is an exhaust port 55 provided in the other end wall 10c, and the exhaust port 55 is communicated with the outside of the pump chamber 10 to increase the compression ratio of the gas. It is also possible to provide the pre-stage vent 51 to be closed by the rotor at the stage where the amount is maximized.

According to this, backflow of exhaust gas can be prevented, overheating of the pump chamber 10 can be suppressed, and pump performance can be improved. Due to the synergistic effect of this backflow prevention effect of the exhaust gas and the cooling effect of the cooling liquid described above, overheating of the pump chamber 10 can be more effectively prevented and pump performance can be improved.

By the way, in this 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 and 30B as disclosed in Patent Document 1 are supported. , 30B from both sides via two rotating shafts 20A, 20B. Furthermore, the present invention can be effectively applied to a packaged rotary pump unit having exhaust ports on both one end wall and the other end wall of the pump chamber body as disclosed in Patent Document 1. However, an exhaust cooling liquid flow path may be provided on one end wall side while maintaining a balance with the exhaust cooling liquid flow path provided on the other end wall side.

Furthermore, in the present invention, for example, by adjusting and managing the temperature of the coolant, it is possible to expand the range of use of the present invention to correspond to use in cold regions, and heat exchange can be performed to circulate the coolant. Of course, additional management methods and configurations used in liquid cooling systems can be selectively adopted as appropriate, such as a configuration in which the cooling liquid can be cooled using a container.

Although the present invention has been variously explained above using preferred embodiments, the present invention is not limited to these embodiments, and it goes without saying that many modifications can be made without departing from the spirit of the invention. It is about.

1 Sealed housing 1a Housing frame portion 1b Base portion 1c Housing cover portion 2 Rotary pump 3 Electric motor 3a Rotating shaft 3b Coupling 3c Safety cover 4 Coolant supply source 4a Coolant supply connection port 4b Coolant supply pipe 4c Cooling Liquid discharge piping 4d Cooling liquid discharge connection port 5 Liquid cooling heat exchanger 5a Pipe line for heat exchange 5b Cooling liquid connection pipe 6 Air blower 7 Air blower fan 8 Switchboard 9 Air blower for cooling electrical components 10 Pump room 10a Cylinder part 10b One side End wall part 10c Other end wall part 11 Cylinder case 12 Side plate 14 Intake connection port 15 Intake port 16 Intake introduction pipe connection port 17 Intake adjustment pipe 20A Rotation shaft (drive side rotation shaft)
20B Rotating shaft (driven side rotating shaft)
21A Gear (drive side gear)
21B Gear (driven gear)
25 Pump cover part 25a Circulating air inlet part 25b Circulating air outlet part 30A Rotor (drive side rotor)
30B rotor (driven rotor)
31 First muffler part 32 Second muffler part 33 Vibration buffer pipe 34 Exhaust inlet of second muffler part 35 Exhaust outlet of second muffler part 37 Hanging member 40 Bearing part 40a First bearing part 40b 2 bearing part 41 Bearing 42 Oil seal 45 Gear box 50 Exhaust side opening 51 Pre-stage vent 55 Exhaust port 56 Exhaust flow path 57 Exhaust port of first muffler part 60 Cooling gap 61 First flow path forming part 61a Coolant flow path forming surface 61b Coolant flow regulating portion 61c Inner loop matching portion 61d Outer loop matching portion 61e Exhaust flow path forming surface 61f Exhaust path forming wall 61g Loop frame shaped matching portion 62 Second flow path forming portion 62a Exhaust Flow path forming surface 62b Extended flow path forming surface 62c Peripheral matching portion 63 Third flow path forming portion 63a Extension flow path forming surface 65 Seal member 71 Bearing coolant flow path 71a Coolant inlet connection portion 71b Bearing coolant outlet Connection part 71c First connection pipe 72 Exhaust part coolant flow path 72a Exhaust part coolant inlet connection part 72b Coolant inlet 72c Exhaust port surrounding flow path part 72d Exhaust part coolant outlet connection part 72e Second connection pipe 73 Extension coolant flow path 73a Extension coolant inlet connection 73b Extension coolant outlet connection 81 Operation unit 82 Electrical components 83 Inverter device 90 Drain discharge connection 91 Drain pan 92 Drain piping 93 Drain pan for heat exchanger 94 For heat exchanger Drain piping 100 Pump main body 110 Pump chamber body part 115 Column part 120 Bearing body part 121 Structural wall part 121a One structural wall part 121b Other structural wall part 200 Electric rotary pump 300 Vibration damping member

Claims (6)

A package type rotary pump unit comprising: an electric rotary pump including a rotary pump that sucks and exhausts gas; and an electric motor that drives the rotary pump; and a sealed casing containing the electric rotary pump,
The rotary pump is provided with a first muffler section that also serves as an exhaust cooling section in which the exhaust gas is cooled by a coolant supplied from a coolant supply source disposed outside the sealed casing, and that produces a silencing effect. ,
A package type rotary pump characterized in that a second muffler section that introduces the exhaust gas that has passed through the first muffler section and muffles the sound is arranged above the electric rotary pump inside the sealed casing. unit. The second muffler section includes a plurality of sound reduction chambers, and the plurality of sound reduction chambers extend in the same direction as the connection direction of the rotary pump and the electric motor and in the longitudinal direction of the sealed casing. The packaged rotary pump unit according to claim 1, wherein the packaged rotary pump unit is arranged in series. 3. The packaged rotary pump unit according to claim 1, wherein the second muffler section is installed in a suspended state inside the sealed casing. The electric rotary pump is installed in the sealed casing via a vibration damping member, and the first muffler section and the second muffler section are connected via a vibration damping pipe. The packaged rotary pump unit according to any one of claims 1 to 3. 5. The package-type rotating device according to claim 1, wherein the second muffler section is arranged on the back side of the inside of the sealed casing, and the switchboard is arranged on the front side. Pumping unit. a liquid-cooled heat exchanger disposed inside the sealed casing and cooled by receiving a coolant supply from a coolant supply source disposed outside the sealed casing;
Cooling the internal air in the sealed casing, which is disposed inside the sealed casing and includes heated air generated when the air around the rotary pump is heated by operation of the rotary pump, to the liquid-cooled heat exchanger. The package type rotary pump unit according to any one of claims 1 to 5, further comprising a blower device for sending air in such a manner as to cause the air to flow.

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