JP2023013385A - Biaxial rotary pump and claw pump - Google Patents

Abstract

To provide a biaxial rotary pump and a claw pump capable of more effectively preventing a pump body from being superheated with a coolant, and also capable of significantly improving reliability of pump operation.SOLUTION: A biaxial rotary pump comprises: a pump chamber body part 110 comprising a cylinder part 10a, one end wall part 10b, and the other end wall part 10c so as to form a pump chamber 10; two rotational shafts 20A, 20B; two rotors 30A, 30B that rotate mutually in a non-contact manner; and a bearing body part 120 that constitutes a structural wall part in which a bearing part 40 is provided and also constitutes a structural wall part as a gear box 45. Between the pump chamber body part 110 and the bearing body part 120, a pump body 100 is partitioned into the pump chamber body part 110 and the bearing body part 120 so that a cooling gap 60 is formed. A bearing part coolant flow path 71 is provided in a structural wall part 121 located on the pump chamber body part 110 side of the bearing body part 120.SELECTED DRAWING: Figure 1

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a biaxial rotary pump and a claw pump in which two rotors rotate in a non-contact state within a pump chamber having a cross-sectional shape formed by overlapping two circles.

A claw pump, which is an example of a conventional biaxial rotary pump, includes a cylinder that forms a pump chamber, one side plate that closes one end surface of the cylinder, and the other side plate that closes the other end surface of the cylinder, two rotating shafts arranged in parallel in a cylinder and rotated at the same speed in opposite directions; two rotors formed with hook-shaped claws so as to compress the sucked gas by meshing in a non-contact state; Both the one side plate and the other side plate are provided with an intake port communicating with the portion of the pump chamber where the gas in the cylinder is not compressed, and the compressed gas is discharged from both sides through both end faces of the cylinder. The applicant of the present invention has proposed a cylinder having an exhaust port that opens to a portion of the pump chamber where the gas in the cylinder is compressed (see Patent Document 1).

According to this conventional claw pump, by opening the exhaust port in both side plates, the opening area of the exhaust port is doubled compared to the case where the exhaust port is opened only in one side plate, and the exhaust is performed. Since ventilation resistance can be reduced, exhaust efficiency can be improved. As a result, the pump performance can be improved, and the degree of freedom in design can be further improved. This effect appears more effectively when used in a region with a low degree of vacuum.

Further, as shown in FIG. 10, the present applicant has provided a cylinder portion 10a, and a and the other end wall portion 10c provided on the other end surface of the cylinder portion 10a. and two rotating shafts 20A and 20B provided on each of 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 sucked gas. At least one portion of the two rotors 30A and 30B having hooked claw portions formed thereon so as to be able to hold the pump chamber 10 and the one end wall portion 10b and the other end wall portion 10c. A claw pump comprising an exhaust-side opening 50 provided at a position facing a portion in which gas is compressed, wherein the exhaust-side opening 50 is located between the two rotors 30A and 30B The front vent port 51 communicated with the outside of the pump chamber 10 at the front stage where the compression ratio of the gas is maximized by the claws, and the claws of the two rotors 30A and 30B make the gas more than the front stage. and a post-stage exhaust port (exhaust port 55) that is in communication with the pump chamber 10 so as to exhaust air to the outside of the pump chamber 10, and the post-stage exhaust port (exhaust port 55) is connected to the pump chamber. 10, the front vent 51 is closed by the rotor 30A at the stage of maximizing the compression ratio of the gas. A pump chamber body portion provided by end wall portions 10b and 10c provided on both end surfaces of the pump chamber body portion, and the two rotors 30A and 30B are arranged at one ends of the two rotating shafts 20A and 20B, respectively. The pump main body is arranged so that a cooling gap is formed between the bearing body portion provided with the bearing portion 40 for bearing the two rotating shafts 20A and 20B so as to be supported in a cantilevered state by A claw pump (see Patent Document 2) has been proposed, which is characterized by being provided in a divided structure.

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

In addition, in the conventional biaxial rotary pump, as an invention of the Roots pump, a water cooling passage is formed in the exhaust manifold directly connected to both the first and second booster pumps, and water is supplied from the water supply tank. There has been proposed a system in which water is sent to a water cooling passage by a pump, passed through the water cooling passage, cooled by a heat exchanger, and returned to a water supply tank (see Patent Document 3).

JP-A-2011-38476 (page 1, claim 1) Japanese Patent No. 6749714 (Claim 1, Fig. 3, etc.) JP 2010-138725 A ([0039], FIG. 5)

The problem to be solved with respect to the biaxial rotary pump and the claw pump is that, for example, when the vacuum pump is used in a high vacuum range where the ultimate vacuum is closer to the absolute vacuum, the pump body is overheated, It is difficult to further improve the reliability of pump operation.

On the other hand, in a biaxial rotary pump and a claw pump, Patent Document 2 proposes a configuration for preventing the pump chamber from being overheated by suppressing the reverse flow of exhaust gas into the pump chamber. Patent Document 3 proposes water-cooling the exhaust manifold, but does not propose a configuration for more positively and effectively preventing overheating of the pump body using cooling liquid.

SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to more effectively prevent overheating of the pump body by using a cooling liquid even when the vacuum pump is used in a high degree of vacuum, thereby significantly improving the reliability of the operation of the pump. To provide a biaxial rotary pump and a claw pump capable of improving the

The present invention has the following configurations in order to achieve the above object.
According to one aspect of the biaxial rotary pump according to the present invention, a cylinder portion is provided on one end face of the cylinder portion so as to form a pump chamber having a cross-sectional shape in which two circles are partially overlapped. A pump chamber body portion having one end wall portion and the other end wall portion provided on the other end face of the cylinder portion, and a pump chamber body portion arranged in parallel in the pump chamber and driven in opposite directions at the same speed by a pair of gears. two rotating shafts to be rotated, two rotors provided corresponding to the two rotating shafts and arranged in the pump chamber to rotate in a non-contact state with each other, and bearings for the two rotating shafts In a biaxial rotary pump comprising a bearing body portion that constitutes a structural wall portion in which a bearing portion is provided and a structural wall portion that serves as a gearbox containing the pair of gears, the pump chamber body portion and the bearing The pump main body is partitioned into the pump chamber body portion and the bearing body portion so that a cooling gap that can suppress heat conduction is formed between the body portion and the bearing body portion. A structural wall located on the side of the pump chamber body is provided with a bearing cooling liquid flow path for passing the cooling liquid.

Further, according to one aspect of the biaxial rotary pump according to the present invention, it is provided in a horizontal type installed by arranging the two rotating shafts horizontally, and the bearing cooling liquid flow path is provided in the gear It is provided at the lower part of the structural wall portion of the bearing body portion so as to cool the lubricating oil stored in the box so as to pass below the liquid level of the lubricating oil in the stored state at rest. It can be characterized as

Further, according to one aspect of the biaxial rotary pump according to the present invention, an exhaust port of the pump chamber may be provided in a lower portion of the pump chamber body portion.
Further, according to one aspect of the biaxial rotary pump according to the present invention, it is provided in a horizontal type installed by arranging the two rotating shafts horizontally, and the cooling gap is filled from the lower side to the upper side. It can be characterized by comprising an air blowing means for blowing air so as to pass through.

Further, according to one aspect of the biaxial rotary pump according to the present invention, the bearing cooling liquid flow path is arranged in the pump chamber body so that the cooling liquid that has cooled the bearing body cools the pump chamber body. It can be characterized by being connected to a coolant flow path provided in the part.

Further, according to one aspect of the claw pump according to the present invention, it has the configuration of the biaxial rotary pump described above, and the two rotors are rotated in a non-contact state to compress and exhaust the sucked gas. The claw pump is a rotor having a hook-shaped pawl so that the one end wall of the pump chamber body is located on the side of the gear box containing the pair of gears, and the pump chamber At least the other end wall portion of the body portion is provided with an exhaust port for discharging gas, and the other end wall portion of the pump chamber body portion is cooled to cool the other end wall portion of the pump chamber body portion. An exhaust coolant flow path may be provided for passing coolant to cool the exhaust exiting the port.

Further, according to one aspect of the claw pump of the present invention, the cooling liquid flows through the bearing cooling liquid flow path in order from the bearing cooling liquid flow path to the exhaust cooling liquid flow path. It can be characterized in that an exhaust cooling liquid flow path is connected.
Further, according to one aspect of the claw pump according to the present invention, a cooling liquid introduction port for introducing cooling liquid into the exhaust cooling liquid flow path is provided in the vicinity of the exhaust port, and the exhaust cooling liquid flow path is provided in the vicinity of the exhaust port. The formed portion is provided with a cooling liquid flow restricting portion that restricts the flow of the introduced cooling liquid so that the cooling liquid circulates first in the vicinity of the exhaust port. can.

Further, according to one aspect of the claw pump of the present invention, the exhaust cooling liquid flow path is provided on the other end wall of the pump chamber body to cover the outer surface side of the other end wall. a cooling liquid flow path forming surface provided to form the exhaust cooling liquid flow path between the other end wall portion and the outer surface of the other end wall portion; It can be characterized by being provided by arranging the part.
Further, according to one aspect of the claw pump of the present invention, the cooling liquid flow path forming surface of the first flow path forming section and the cooling liquid flow path forming surface are arranged such that the exhaust gas is cooled by the first flow path forming section. An exhaust flow path through which the exhaust gas passes is provided on the side of the outer surface of the first flow path forming portion, which is the opposite surface.

Further, according to one aspect of the claw pump according to the present invention, the exhaust flow path is arranged in the first flow path forming portion so as to cover the outer surface side of the first flow path forming portion. By arranging a second flow passage forming portion which is a portion and which has an exhaust flow passage forming surface provided to form the exhaust flow passage with the outer surface of the first flow passage forming portion , is provided.
Further, according to one aspect of the claw pump according to the present invention, the extension cooling liquid flow path continuing to the exhaust cooling liquid flow path is provided in the second flow path forming section. an extension passage forming surface provided to cover the outer surface side of the second passage forming portion and to form the extension cooling liquid passage with the outer surface of the second passage forming portion It can be characterized by being provided by disposing a third flow path forming portion comprising

Further, according to one aspect of the claw pump according to the present invention, at least one of the one end wall portion and the other end wall portion, in which the gas in the pump chamber is compressed, is provided with a front-stage vent port in which an exhaust-side opening provided at a facing position communicates with the outside of the pump chamber at a front stage where the gas compression ratio is maximized by the claw portions of the two rotors; a post-stage exhaust port that communicates with the pawl portions of the two rotors so as to exhaust gas to the outside of the pump chamber, including a step in which the compression ratio of the gas is maximized more than the gas compression ratio of the preceding stage; A port is the exhaust port provided in the other end wall portion, and the exhaust port communicates with the outside of the pump chamber to maximize the compression ratio of the gas, and the front vent port is connected to the rotor. It can be characterized in that it is provided to be closed by

INDUSTRIAL APPLICABILITY According to the biaxial rotary pump and the claw pump according to the present invention, overheating of the pump body can be more effectively prevented by using the coolant even when used as a vacuum pump in a high vacuum range. , there is a particularly advantageous effect that the reliability of the pump operation can be significantly improved.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional perspective view showing a stepwise cutaway state showing an internal structure of a claw pump, which is an example of a biaxial rotary pump according to the present invention. FIG. 2 is a front perspective view of the embodiment of FIG. 1; FIG. 2 is a rear side perspective view of the embodiment of FIG. 1; 2 is a front view of the embodiment of FIG. 1; FIG. 2 is a rear view of the embodiment of FIG. 1; FIG. 2 is a plan view of the embodiment of FIG. 1; FIG. FIG. 2 is a cross-sectional perspective view showing a bearing cooling liquid flow path in the embodiment of FIG. 1; FIG. 2 is an exploded view showing a coolant flow path forming surface, which is an inner surface of a first flow path forming portion in the embodiment of FIG. 1; 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; 1 is an exploded view showing a conventional claw pump; FIG.

Embodiments of a biaxial rotary pump and a claw pump according to the present invention will be described in detail below with reference to the accompanying drawings (FIGS. 1 to 9). An example of the form of the biaxial rotary pump according to the present invention is a vacuum pump, which is a water-cooled claw pump. It can also be used as a blower, etc., and can be used as a cooling liquid other than water.

As shown in FIG. 1, etc., in the claw pump according to the present invention, reference numeral 110 denotes a pump chamber body portion, which forms a cross-sectional shape of the pump chamber 10 (see FIG. 10) by partially overlapping two circles. Further, it has 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 are arranged in parallel in the pump chamber 10 and are 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 the 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. As shown in FIG.

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 sucked gas. A hook-shaped claw portion is formed and provided as shown in FIG. 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 claw pump, which is a type of biaxial rotary pump.

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

In the claw pump according to the present invention, the other end wall portion 10c side of the pump chamber body portion 110 is provided with an exhaust cooling liquid for passing the cooling liquid so as to cool the exhaust discharged from the exhaust port 55. A flow path 72 is provided. It should be noted that, in this embodiment (an example of use as a vacuum pump), the state in which the exhaust is discharged from the exhaust port 55 means that the pump chamber 10 is open and communicated with the atmosphere (air), which is the outside air. state, and the exhaust will be released into the atmosphere (air). Cooling liquid is typically cooling water, but it goes without saying that liquids other than water can also be used, including mixtures (aqueous solutions) with water, such as antifreeze, and oil. be.

According to the claw pump of the present invention, even when the vacuum pump is used in a high vacuum range in which the ultimate vacuum is closer to the absolute vacuum, overheating of the pump chamber 10 can be prevented more positively. In addition, it can be effectively prevented, and the pump performance can be remarkably improved.

That is, by providing the exhaust cooling liquid flow path 72 on the side of the other end wall section 10c of the pump chamber body section 110, the cooling liquid can effectively cool the exhaust immediately after being discharged from the exhaust port 55. can. According to this, even if the vacuum pump is used in a high vacuum range above a certain level and the pump chamber 10 is heated due to the reverse flow of the exhaust gas, it is possible to suppress the increase in the internal temperature of the pump chamber 10 . For this reason, it is possible to set a small clearance for non-contact between the inner wall surface of the pump chamber 10 and the two rotors 30A and 30B. can improve.

Further, according to the claw pump according to the present invention, the clearance can be set small as described above, so that the degree of ultimate vacuum can be further increased, and overheating can be prevented even if there is a backflow of exhaust gas, so that the exhaust port 55 can be prevented from overheating. Since the opening area can be set wider, a vacuum pump with a larger processing air volume can be configured.

According to the claw pump of this embodiment, the other end wall portion 10c provided with the exhaust port 55, which is the most heated, is actively and locally cooled. That is, the other wall portion of the pump chamber body portion 110 centered on the exhaust port 55 is adjusted so as to reduce the temperature difference with respect to the pump chamber body portion 110 in which the temperature gradient (temperature difference) is large. The exhaust gas is cooled by preferentially cooling the 10c side. By cooling the exhaust gas in this way to prevent overheating of the pump chamber 10, it has been confirmed that the internal temperature difference can be reduced by about 140° C., and the ultimate vacuum can be increased to 97 kPa. It is possible to significantly improve the pump performance. Conventionally, as the limit for the continuous operation, the ultimate vacuum is up to about 90 kPa in order to avoid contact (internal interference) between the inner wall surface of the pump chamber 10 and the two rotors 30A and 30B. was only able to drive In contrast, according to the present invention, it is possible to continuously perform shut-off operation with a higher ultimate vacuum.

By the way, in the claw pump, since the compressibility 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 portion of the other end wall portion 10c in which the exhaust port 55 is formed. becomes hotter than other parts. Then, compared with the other end wall portion 10c, the other portion of the pump chamber body portion 110 has a lower temperature. Therefore, if the entire pump chamber body portion 110 including the cylinder portion 10a and the like is cooled in the same manner, the temperature difference between the exhaust port 55 of the other end wall portion 10c and the other portions is maintained. Therefore, the problem that the rotors 30A and 30B, which are moving parts, interfere with each other due to thermal expansion cannot be solved.

Further, according to this embodiment, the cooling liquid introduction port 72b for introducing the cooling liquid into the exhaust cooling liquid flow path 72 is provided near the exhaust port 55, and is located at the portion where the exhaust cooling liquid flow path 72 is formed. is provided with a cooling liquid flow regulating portion 61b that regulates the flow of the introduced cooling liquid so that the cooling liquid circulates in the vicinity of the exhaust port 55 first. As shown in FIG. 8, the coolant flow regulating portion 61b of this embodiment is provided at a plurality of locations (two locations in this embodiment) on the coolant flow path forming surface 61a of the first flow path forming portion 61, which will be described later. It is provided in a form protruding like a rib.

According to this, by cooling the portion around the exhaust port 55, which is the most heated portion of the pump chamber body portion 110 (surrounding the exhaust port 55), the exhaust immediately after the exhaust port can be effectively cooled. By lowering the temperature of the periphery of the exhaust port 55 and the temperature of the exhaust gas, it is possible to prevent the periphery of the exhaust port 55 from being excessively heated and unevenly deformed due to thermal expansion in a well-balanced manner. In this manner, 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, so the mutual clearance therebetween can be reduced and the pump efficiency can be improved.

In the claw pump, 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) in terms of driving stability. In this embodiment, the cooling liquid inlet 72b is provided as described above, and the portion of the exhaust cooling liquid flow path 72 near the exhaust port 55 located below the other end wall portion 10c is further expanded. The cooling liquid having a lower temperature is first cooled, and the cooling liquid that has cooled the other end wall portion 10c in this manner is discharged upward through the exhaust cooling liquid outlet connection portion 72d. At this time, the cooling liquid is heat-exchanged and its temperature rises, so that the specific gravity of the cooling liquid becomes smaller and an upward flow vector is generated. According to this flow of the cooling liquid, the portion of the lower exhaust port 55 can be effectively cooled, and the directionality of the flow due to the temperature rise of the cooling liquid and the directionality of the flow for discharging the cooling liquid upward can be changed. can be aligned. Therefore, the cooling liquid can pass through smoothly, and the cooling efficiency can be effectively improved.

Further, according to this embodiment, the exhaust cooling liquid flow path 72 is arranged in 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 having a cooling liquid flow path forming surface 61a provided to form the exhaust cooling liquid flow path 72 with the outer surface of the other end wall portion 10c. is provided by placing According to this, the exhaust cooling liquid flow path 72 can be configured effectively and rationally.

As shown in FIGS. 1, 8, and 9, the first flow path forming portion 61 of this embodiment is provided by a board-like 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 by bolts, and is provided so that the mating portion is water-tightly sealed by a seal member 65 to form an exhaust portion coolant flow path 72. As shown in FIG. The joining portion of this embodiment includes an inner loop joining portion 61c formed in a rectangular loop frame shape surrounding the exhaust port 55 so as to extend the exhaust path of the exhaust port 55, and a peripheral portion of the other end wall portion 10c. and an outer loop joint portion 61d formed so as to abut against the loop frame shape. Between the inner loop mating portion 61c and the outer loop mating portion 61d, an exhaust cooling liquid flow path 72 is formed and is filled with cooling liquid. According to this configuration, the outer wall surface of the other end wall portion 10c is brought into contact with the cooling liquid over the entire surface to enable efficient cooling. In addition, this structure has a form in which the layered exhaust cooling liquid flow path 72 is planarly stacked on the outside of the outer end surface of the pump chamber body 110, and has a compact configuration.

In addition, in the first flow path forming portion 61 of the present embodiment, one portion of the exhaust portion cooling liquid flow path 72 is provided on the cooling liquid flow path forming surface 61a that faces (faces) the outer surface of the other end wall portion 10c. A passage forming wall constituting the cooling liquid flow restricting portion 61b is provided in a protruded form so that an exhaust port surrounding passage portion 72c, which 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. , a passage forming wall (coolant flow restricting portion 61b) for appropriately bending and guiding the exhaust portion coolant flow path 72 is provided. In addition, the present invention is not limited to this, and it is also possible to appropriately provide a passage forming wall on the side of the outer surface of the other end wall portion 10c.

Further, according to this embodiment, the surface opposite to the cooling liquid flow path forming surface 61 a of the first flow path forming section 61 is arranged so 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 61 e that is the outer surface of the first flow path forming portion 61 . That is, the exhaust channel 56 is a channel connected to the exhaust port 55 and a channel through which the exhaust discharged from the exhaust port 55 passes.

According to this exhaust flow path 56, the overheated exhaust gas can be effectively cooled, and the temperature in the pump chamber 10 is lowered by lowering the temperature of the exhaust gas. Overheating and thermal expansion of the two rotors 30A and 30B can be suppressed in a well-balanced manner.
In addition, the exhaust flow path 56 can appropriately regulate the direction of the flow of the exhaust gas, and has a form for promoting the cooling of the exhaust gas, and also serves as a muffler structure for reducing exhaust noise. It has become. A muffler exhaust port 57 is opened in the upper wall portion of the first flow path forming portion 61 and serves as an exhaust port for an exhaust flow path 56. be done. As shown in FIG. 9, the muffler exhaust port 57 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 silencing 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, and By arranging the second flow path forming portion 62 having 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 section 61, 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. . In addition, this structure has a form in which the layered exhaust passages 56 are planarly stacked on the outside of the outer end surface of the pump chamber body portion 110, and thus has a compact structure.

In addition, as shown in FIG. 1 and the like, 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 contacts the outer surface side of the first flow path forming portion 61). A plate-like member 62a is formed flat, and is fixed to the outer surface (exhaust flow path forming surface 61e) side of the first flow path forming portion 61 by bolts. Further, on the side of the outer surface (exhaust flow path forming surface 61e) of the first flow path forming portion 61 with respect to the exhaust flow path forming surface 62a (flat surface), a groove-like groove that becomes the exhaust flow path 56 is provided. The exhaust passage forming wall 61f is provided in a projecting form so as to form a passage. Then, the loop frame-shaped mating portion 61g and the exhaust passage forming wall 61f of the outer peripheral portion, which is 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 fixed by close contact. It can be naturally airtight, or it can be airtight by placing a sealing member. 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. 9, the exhaust flow path 56 is formed in a complicatedly curved flow path, so that the cooling of the exhaust gas can be further promoted, and the muffler chamber functions appropriately to further reduce the exhaust noise. can be reduced.

Furthermore, according to this embodiment, the extension cooling liquid flow path 73 that is continuous with the exhaust cooling liquid flow path 72 is formed in the second flow path forming section 62 on the outer surface of the second flow path forming section 62 ( It is a part arranged so as to cover the side of the extension flow path forming surface 62b), and the extension part cooling liquid flow path is formed between the outer surface (extension flow path forming surface 62b) of the second flow path forming part 62 and It is provided by disposing a third flow path forming portion 63 having an extended flow path forming surface 63 a provided to form 73 . According to this, the extension cooling liquid flow path 73 can be configured effectively and rationally. In addition, this structure has a form in which the layered extension cooling liquid flow paths 73 are stacked on the outside of the outer end face of the pump chamber body 110 in a planar manner, resulting in a compact configuration. In addition, the layered extension coolant flow path 73 and the structural walls that form it can reduce noise.

In addition, as shown in FIG. 1 and the like, the third flow path forming portion 63 of this embodiment is provided by a flat plate-like member (plate member), and the second flow path forming portion 62 is secured by bolts. , and is watertightly sealed by a sealing member 65 to the peripheral edge joint portion 62c provided in the shape of a loop frame on the outer surface of the second flow path forming portion 62, so that the extension portion coolant flow path 73 is formed. is provided in In addition, in this embodiment, the cooling liquid is retained in the flat layered space of the extension cooling liquid flow path 73. However, the present invention is not limited to this, and any suitable configuration can be used. Needless to say, the flow path may be set at . Furthermore, it is also possible to increase the cooling performance by multilayering the extension cooling liquid flow path 73 . Also, in the extension cooling liquid flow path 73, similarly to the exhaust cooling liquid flow path 72, the upper portion of the second connection pipe 72e is arranged so that the cooling liquid flows from the bottom to the top. From the exhaust cooling liquid outlet connection 72d provided and connected to the exhaust cooling liquid flow path 72, the second connection is provided to the extension cooling liquid inlet connection 73a provided in the lower part of the second connecting pipe 72e. An extension cooling liquid outlet connection portion 73b is provided at the upper portion so that the cooling liquid flowing through the extension cooling liquid flow path 73 is discharged to the outside.

By the way, in this embodiment, the pump chamber 10 includes the cylinder case 11 integrally provided with the cylinder portion 10a, one end wall portion 10b, and one structural wall portion 121a provided with the first bearing portion 40a. , and the 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, but is not limited to this. Of course, it may be formed by mainly three divided members.

Next, in the biaxial rotary pump according to the present invention, an example of a configuration for cooling the bearing portion 40 that supports the two rotary shafts 20A and 20B will be described in detail with reference to the accompanying drawings (FIGS. 1 to 9). do. As described above, the biaxial rotary pump of this embodiment is a claw pump, but the present invention is not limited to this, and other biaxial rotary pumps such as roots pumps and screw pumps can also be used. Applicable. Further, in the biaxial rotary pump according to the present invention, the two rotors 30A and 30B are not limited to the form in which the two rotors 30A and 30B are supported in a cantilevered state, 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 is freely supported.

In the biaxial rotary pump according to the present invention, as shown in FIG. 1, the structural wall portion 121 provided with the bearing portion 40 for bearing the two rotating shafts 20A and 20B is configured, and the two rotating shafts 20A and 20B It comprises a bearing body portion 120 forming a structural wall portion 121 as a gearbox 45 enclosing a pair of correspondingly provided gears 21A, 21B in mesh. 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 rotation shafts 20A (drive-side rotation shaft) and 20B (driven-side rotation shaft). Bearing portions 40 for bearing the rotating shafts 20A and 20B are provided so as to be respectively arranged at one end and supported in a cantilevered state. The bearing body portion 120 and the pump chamber body portion 110 constitute the pump main body 100 of the biaxial rotary pump.

The pump main body 100 is arranged between the pump chamber body portion 110 and the bearing body portion 120 so that a cooling gap 60 capable of suppressing heat conduction is formed between the pump chamber body portion 110 and the bearing body portion 120 . The structural wall portion 121 (one structural wall portion 121a in this embodiment) located on the side of the pump chamber body portion 110 of the bearing body portion 120 is provided so as to be partitioned into the bearing portion cooling for passing the cooling liquid. A liquid flow path 71 is provided.

According to this, along with the 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 portion 120, the coolant passing through the bearing portion coolant flow path 71 is reduced. This cooling effect provides a particularly advantageous effect of prolonging the life of the functional parts constituting the bearing portion 40 and the like. That is, according to the present invention, by providing the gap 60 for cooling by partitioning the pump chamber body portion 110 and the bearing body portion 120, heat conduction can be suppressed so as to minimize the amount of heat transfer, and the bearing portion Since the bearing body portion 120 can be cooled more positively by the coolant flowing through the coolant 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.
The functional parts are components including the bearing 41 and the oil seal 42, and are treated as consumable parts. Running costs can be reduced by prolonging the life of these functional parts.

By the way, the bearing portion 40 of the present embodiment has the pump chamber body portion 110 in the bearing body portion 120 so as to support the two rotating shafts 20A and 20B between the two gears 21A and 21B and the two rotors 30A and 30B. The first bearing portion 40a provided on the side structural wall portion (one structural wall portion 121a) and the structural wall portion opposite to the first bearing portion 40a, which is a driving motor (not shown), are connected. The structural wall portion (the other structural wall portion 121b) disposed on the opposite side is configured by a second bearing portion 40b provided so as to bear the two rotating shafts 20A and 20B. The rotating shaft of the drive motor is connected to the rotating shaft 20A (driving side rotating shaft) via a coupling.

Further, in this embodiment, the two rotating shafts 20A and 20B are provided in a horizontal type installed by arranging them horizontally, and the bearing cooling liquid flow path 71 is a lubricating oil stored in the gear box 45. is provided in the lower portion of the structural wall portion 121 of the bearing body portion 120 so as to pass below the liquid surface of the lubricating oil in the stored state at rest so as to cool the oil. The liquid level of the lubricating oil when it is stationary is set to be 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 scooped up by the two rotating gears 21A, 21B to lubricate the gears 21A, 21B and the bearing 41, and to lubricate the inside of the gear box 45. can be cooled.

In this embodiment, the bearing cooling liquid flow path 71 is provided in the bearing body 120 under the first bearing 40a (below the bearing 41 of the first bearing 40a). It is provided in the shape of a through hole, and is locally arranged. According to this, it is possible to positively cool the portion of the bearing body portion 120 to which heat is easily conducted from the pump chamber body portion 110 side, and to effectively cool the lubricating oil.

Furthermore, in this embodiment, the exhaust port of the pump chamber is provided in the lower portion of the pump chamber body portion. According to this, when the bearing cooling liquid flow path 71 is provided in the lower portion 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 Overheating can be suppressed.

Further, in addition to the configuration provided in the horizontal type installed by arranging the two rotating shafts 20A and 20B horizontally as in this embodiment, the cooling gap 60 is provided from the bottom to the top. A blowing means for blowing 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 flow appropriately between the pump chamber body portion 110 and the bearing body portion 120, heat transfer can be suppressed more effectively, and cooling by heat radiation can be promoted. As a result, the temperature rise of the bearing body portion 120 can be suppressed, and the life of the functional parts can be extended.

According to the biaxial rotary pump of the present invention, the bearing cooling liquid flow path 71 is provided in the pump chamber body section 110 so that the cooling liquid that has cooled the bearing body section 120 cools the pump chamber body section 110 . It can be characterized in that it is connected to a cooling liquid flow path. According to this, in order to prevent the lubricating oil from boiling and overheating, the temperature of the cooling liquid flowing through the bearing section cooling liquid flow path 71 is higher than that of the cooling liquid flow path provided in the pump chamber body section 110. The temperature can be lower than the temperature of the flowing coolant, and the coolant can be effectively utilized.

Further, in this embodiment, the exhaust cooling liquid flow path 72 is connected to the bearing cooling liquid flow path 71 so that the cooling liquid flows in order from the bearing cooling liquid flow path 71 to the exhaust cooling liquid flow path 72. It is According to this, one cooling liquid supply source (not shown) is used for the structural wall portion 121 (one structural wall portion 121a) constituting the bearing portion 40 (first bearing portion 40a) of the bearing body portion 120. , and the other end wall portion 10c of the pump chamber body portion 110 can be directly and sequentially cooled effectively. In addition, the cooling liquid of this embodiment is supplied from a cooling liquid supply source (not shown), and the cooling liquid inlet connection portion 71a (FIGS. 3, 5, and 7), the bearing portion cooling liquid flow path 71 (FIG. 1 , FIG. 7), the bearing cooling liquid outlet connecting portion 71b (FIGS. 2, 4, 6, and 7), and then the first connecting pipe 71c (FIGS. 2, 4, 6, and 7). ), the exhaust cooling liquid inlet connecting portion 72a (FIGS. 2, 4 and 6), the cooling liquid inlet 72b (FIG. 8), and supplied to the exhaust cooling liquid flow path 72 (FIGS. 1 and 8). It is designed to be Without being limited to this, the cooling liquid may be supplied separately without connecting the bearing cooling liquid flow path 71 and the exhaust cooling liquid flow path 72, and the cooling liquid supply may be individually adjusted. It may be optimized by

In addition, in the flow path constituted by the bearing cooling liquid flow path 71, the exhaust cooling liquid flow path 72, and the extension cooling liquid flow path 73, the exhaust cooling liquid flow path 71 is located above the bearing cooling liquid flow path 71. The cooling liquid flow path 72 is provided, and the cooling liquid flows from the bottom to the top in the exhaust cooling liquid flow path 72 and the extension cooling liquid flow path 73. By aligning the properties and the directionality of the flow of the cooling liquid, the cooling liquid can flow smoothly, and the bearing portion 40 and the exhaust gas can be cooled effectively.

According to the cooling structure of the biaxial rotary pump described above, it is possible to rationally respond to the claw pump and improve the cooling performance, thereby improving the pump performance. Further, in the claw pump according to the present invention, the lower side of the pump chamber 10 is easily overheated, and a structure capable of cooling from the lower side can be appropriately formed as described above. As a result, the pump chamber 10 can be efficiently cooled, the performance of the pump can be improved, and a particularly advantageous effect can be obtained in that the service life of the functional parts can be extended as described above.

In this embodiment, as shown in FIGS. 1 to 7, the cooling gap 60 between the pump chamber body portion 110 and the bearing body portion 120 includes one end wall portion 10b and one end wall portion 10b. A plurality of columnar portions 115 are provided to integrate with one structural wall portion 121a provided with the first bearing portion 40a facing the portion 10b. It is provided so that the gap 60 for cooling is formed in the portion where it does not exist. For example, when such a shape is manufactured by casting, the cooling gap 60 may be formed by a core. Moreover, the present invention is not limited to this, and as shown in FIG. The members on the bearing body portion 120 side that constitute the structural wall portion 121 of the portion 40 are composed of separate members and are connected by columnar connection portions 111 and 122 formed on both sides, thereby forming a cooling gap 60. Of course you can.

Further, in the claw pump according to the present invention, in addition to the configuration described above, at least one of the one end wall portion 10b and the other end wall portion 10c is provided with the gas in the pump chamber 10. The exhaust-side opening 50, which is open at a position facing the part where the rotor 30A and 30B are compressed, is provided outside the pump chamber 10 before the gas compression ratio is maximized by the claws of the two rotors 30A and 30B. The front stage ventilation port 51 communicated with the rear stage communicated with the claw portions of the two rotors 30A and 30B so as to exhaust the gas to the outside of the pump chamber 10, including the step of maximizing the compression ratio of the gas compared to the front stage. The subsequent exhaust port is an exhaust port 55 provided in the other end wall portion 10c, and the exhaust port 55 communicates with the outside of the pump chamber 10 to maximize the gas compression ratio. The front vent 51 may be closed by the rotor during the step.

According to this, it is possible to prevent the exhaust gas from flowing backward, suppress the overheating of the pump chamber 10, and improve the pump performance. Due to the synergistic effect of the backflow prevention effect of the exhaust gas and the cooling effect of the cooling liquid, 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. , 30B are supported from both sides via two rotary shafts 20A and 20B. Moreover, it can also be effectively applied to a claw pump having exhaust ports on both one end wall portion and the other end wall portion of a pump chamber body portion as disclosed in Patent Document 1. After balancing with the exhaust cooling liquid flow path provided on the other end wall side, the exhaust cooling liquid flow path may be provided on one end wall side as well.

Further, in the present invention, for example, by adjusting and managing the temperature of the cooling liquid, it is possible to expand the range of use of the present invention in response to use in cold regions, and heat exchange is performed by circulating the cooling liquid. Of course, additional control methods and configurations used for liquid cooling can be selectively adopted as appropriate, such as a configuration in which the cooling liquid is cooled using a device.

Although the present invention has been described in various ways with preferred embodiments, the present invention is not limited to these embodiments, and many modifications can be made without departing from the spirit of the invention. It's about.

REFERENCE SIGNS LIST 10 pump chamber 10a cylinder portion 10b one end wall portion 10c the other end wall portion 11 cylinder case 12 side plate 14 intake connection port 15 intake port 20A rotating shaft (drive-side rotating shaft)
20B rotary shaft (driven side rotary shaft)
21A gear (drive side gear)
21B gear (driven side gear)
30A rotor (drive side rotor)
30B rotor (driven rotor)
40 Bearing portion 40a First bearing portion 40b Second bearing portion 41 Bearing 42 Oil seal 45 Gear box 50 Exhaust side opening 51 Front vent 55 Exhaust port 56 Exhaust flow path 57 Muffler exhaust port 60 Cooling gap 61 Second 1 channel forming portion 61a cooling liquid channel forming surface 61b cooling liquid flow restricting portion 61c inner loop joining portion 61d outer loop joining portion 61e exhaust channel forming surface 61f exhaust passage forming wall 61g loop frame joining portion 62 second Flow path forming part 62a Exhaust flow path forming surface 62b Extension flow path forming surface 62c Peripheral edge matching part 63 Third flow path forming part 63a Extension flow path forming surface 65 Sealing member 71 Bearing cooling fluid flow path 71a Cooling fluid inlet connecting part 71b Bearing cooling liquid outlet connection 71c First connection pipe 72 Exhaust cooling liquid flow path 72a Exhaust cooling liquid inlet connection 72b Cooling liquid introduction port 72c Exhaust surrounding flow path section 72d Exhaust cooling liquid outlet connection 72e second connection pipe 73 extension coolant flow path 73a extension coolant inlet connection 73b extension coolant outlet connection 100 pump body 110 pump chamber body 115 column 120 bearing body 121 structural wall 121a Structural wall 121b Other structural wall

Claims (13)

A cylinder part, one end wall part provided on one end face of the cylinder part, and a a pump chamber body portion provided with the other end wall portion;
two rotary shafts arranged in parallel in the pump chamber and rotated in opposite directions at the same speed by a pair of gears;
two rotors arranged in the pump chamber corresponding to the two rotating shafts and rotated in a non-contact manner with each other;
A biaxial rotary pump comprising: a bearing body portion that constitutes a structural wall portion in which bearing portions for bearing the two rotating shafts are provided, and a bearing body portion that constitutes a structural wall portion serving as a gearbox containing the pair of gears;
The pump main body is partitioned into the pump chamber body portion and the bearing body portion so that a cooling gap capable of suppressing heat conduction is formed between the pump chamber body portion and the bearing body portion. provided,
A biaxial rotary pump, wherein a structural wall portion of the bearing body portion located on the side of the pump chamber body portion is provided with a bearing portion cooling liquid flow path for passing the cooling liquid. Provided in a horizontal type installed by arranging the two rotating shafts horizontally,
The bearing body portion is configured so that the bearing portion cooling fluid flow path passes below the liquid level of the lubricating oil in the stored state at rest so as to cool the lubricating oil stored in the gear box. 2. The biaxial rotary pump according to claim 1, wherein the pump is provided under the structural wall of the. 3. The biaxial rotary pump according to claim 2, wherein an exhaust port of said pump chamber is provided in a lower portion of said pump chamber body. Provided in a horizontal type installed by arranging the two rotating shafts horizontally,
The biaxial rotary pump according to any one of claims 1 to 3, further comprising blowing means for blowing air so as to pass from the lower side to the upper side in the cooling gap. The bearing portion coolant flow path is connected to a coolant flow path provided in the pump chamber body portion so that the coolant that has cooled the bearing body portion cools the pump chamber body portion. The biaxial rotary pump according to any one of claims 1 to 4. The two rotors are hook-shaped so as to compress and discharge the sucked gas by rotating in a non-contact state with each other. A claw pump that is a rotor provided with claws,
The one end wall portion of the pump chamber body portion is located on the side of the gear box containing the pair of gears, and at least the other end wall portion of the pump chamber body portion is provided with an exhaust port for discharging gas. be
Exhaust cooling for passing coolant through the other end wall of the pump chamber body so as to cool the other end wall and thereby cool the exhaust discharged from the exhaust port. A claw pump, comprising a liquid flow path. The exhaust cooling liquid flow path is connected to the bearing cooling liquid flow path so that the cooling liquid flows in order from the bearing cooling liquid flow path to the exhaust cooling liquid flow path. 7. The claw pump of claim 6. A cooling liquid introduction port for introducing cooling liquid into the exhaust cooling liquid channel is provided near the exhaust port, and a cooling liquid is provided in the vicinity of the exhaust port at a portion where the exhaust cooling liquid channel is formed. 8. A claw pump according to claim 6 or 7, further comprising a cooling liquid flow regulating portion for regulating the flow of the introduced cooling liquid so that the cooling liquid circulates first. The exhaust part cooling liquid flow path is a part arranged in the other end wall part of the pump chamber body part so as to cover the outer surface side of the other end wall part, and the other end wall part A first flow path forming part having a cooling liquid flow path forming surface provided to form the exhaust cooling liquid flow path between the outer surface of the The claw pump according to any one of claims 6 to 8. an outer surface of a first flow path forming portion opposite to the cooling liquid flow path forming surface of the first flow path forming portion so that the exhaust gas is cooled by the first flow path forming portion; 10. The claw pump according to claim 9, wherein an exhaust passage through which the exhaust gas passes is provided on the side of . The exhaust flow path is a portion arranged in the first flow path forming portion so as to cover the outer surface side of the first flow path forming portion and the outer surface of the first flow path forming portion. 11. The method according to claim 10, characterized by being provided by disposing a second flow path forming portion having an exhaust flow path forming surface provided to form the exhaust flow path between claw pump. An extension cooling liquid flow path that is continuous with the exhaust cooling liquid flow path is a portion that is arranged in the second flow path forming section so as to cover the outer surface side of the second flow path forming section. a third flow path forming portion having an extension flow path forming surface provided to form the extension cooling liquid flow path between itself and the outer surface of the second flow path forming portion; 12. The claw pump of claim 11, wherein . an exhaust-side opening provided at a position facing a portion of at least one of the one end wall portion and the other end wall portion where gas is compressed in the pump chamber; a front-stage vent communicating with the outside of the pump chamber at the front stage where the gas compression ratio is maximized by the claw portions of the two rotors; and a post-stage exhaust port communicating with the exhaust to the outside of the pump chamber including the step of maximizing the compression ratio of the pump chamber, wherein the post-stage exhaust port is provided in the other end wall portion of the exhaust and said front vent is closed by said rotor at a stage in which said exhaust port communicates with the outside of said pump chamber to maximize the compression ratio of gas. 13. The claw pump according to any one of 12.

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