WO2021085282A1

WO2021085282A1 - Claw pump

Info

Publication number: WO2021085282A1
Application number: PCT/JP2020/039646
Authority: WO
Inventors: 智之小出; 恵一丸山; 小林　和也
Original assignee: オリオン機械株式会社
Priority date: 2019-10-28
Filing date: 2020-10-22
Publication date: 2021-05-06
Also published as: DE112020000151T5; JP2021067245A; CN113260791B; JP6749714B1; CN113357146A; CN113260791A; CN113357146B; KR20220081950A

Abstract

Provided is a claw pump that enables a pump chamber to be prevented from overheating even when the pump is used in a high range of degrees of vacuum, as a vacuum pump, and that enables remarkable improvement of pump efficiency. The present invention is provided with: a pump chamber 10 that is formed by a cylinder part 10a, one end wall part 10b, and another end wall part 10c; two rotary shafts 20A, 20B; two rotors 30A, 30B having hook-shaped claw parts formed therein such that suctioned gas can be compressed and exhausted; and an exhaust-side opening part 50 that is provided in at least one portion of the one end wall part 10b and the other end wall part 10c to be open at a position facing a portion where gas in the pump chamber 10 is compressed. The exhaust-side opening part 50 is obtained by disposing a former-step ventilation hole 51 connected to the outside of the pump chamber 10 at a former step in which the gas compression ratio is maximized and a latter-step exhaust hole 52 that includes a stage where the gas compression ratio is maximized as compared with that at the former step and that is connected for exhaust to the outside of the pump chamber 10.

Description

Claw pump

The present invention relates to a claw pump including a pump chamber having a cross-sectional shape in which a part of two circles is overlapped, and two rotors having hook-shaped claws formed so that the inhaled gas can be compressed and exhausted. ..

In a conventional claw pump, a cylinder forming a pump chamber, one side plate that closes one end face of the cylinder, and the other side plate that closes the other end face of the cylinder are located parallel to each other in the cylinder. Two rotating shafts that are arranged in the same direction and rotate at the same speed in opposite directions, and two rotating shafts that are integrally fixed to each of the two rotating shafts and arranged in the cylinder, mesh with each other in a non-contact state and suck. Two rotors having hook-shaped claws formed so that the gas can be compressed, a rotary drive device for rotationally driving the two rotors via the two rotating shafts, and a rotary driving device in which the gas in the cylinder is not compressed. The gas in the cylinder is compressed by both the one side plate and the other side plate so that the compressed gas is discharged from both sides through the intake port communicating with the portion of the pump chamber and both end faces of the cylinder. Applicants have proposed one provided with an exhaust port that opens in a portion of the pump chamber (see Patent Document 1).

According to this conventional claw pump, the opening area of the intake port can be doubled to reduce the ventilation resistance of the exhaust, so that the 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 is more effective when used in a region where the degree of vacuum is low.

Japanese Unexamined Patent Publication No. 2011-38476 (page 1, claim 1)

The problem to be solved regarding the claw pump is that when the vacuum pump is used in a high vacuum range where the ultimate vacuum is closer to the absolute vacuum, the pump chamber is overheated and the pump efficiency is improved. It's difficult. That is, when the claw pump is used in a high vacuum range, the pressure inside the pump is lower than the external pressure (for example, atmospheric pressure), so that the exhaust gas discharged at the exhaust port may flow back. is there. Then, the backflow exhaust gas is heated and discharged by being compressed in the pump chamber, and is originally at a high temperature, and is recompressed and reheated in the inflowing pump chamber by the backflow. As a result, the pump chamber is further overheated. When the pump chamber is overheated, thermal expansion causes the rotating rotors and the rotors to interfere with each other and constituent members such as a cylinder forming the pump chamber, which causes a failure. In order to prevent this, it becomes necessary to increase the mutual clearance of the constituent members, and the pump performance cannot be improved.

Therefore, an object of the present invention is to provide a claw pump as a vacuum pump, which can prevent the pump chamber from being overheated and improve the pump efficiency even when used in a range of high vacuum degree. ..

The present invention includes the following configurations in order to achieve the above object.
According to one form of the claw pump according to the present invention, the cylinder portion and one end surface of the cylinder portion are provided so as to form a pump chamber having a cross-sectional shape in which a part of two circles is overlapped. Two rotating shafts provided with an end wall portion and the other end wall portion provided on the other end surface of the cylinder portion, arranged in parallel in the pump chamber and rotated at the same speed in opposite directions, and the two. Two rotors provided in each of the two rotating shafts, arranged in the pump chamber, and having hook-shaped claws formed so that the inhaled gas can be compressed and exhausted by rotating in a non-contact state with each other. An exhaust side opening provided at least one of the one end wall portion and the other end wall portion at a position facing the portion where the gas is compressed in the pump chamber. A claw pump including the above, wherein the exhaust side opening communicates with the outside of the pump chamber in the pre-stage where the compression ratio of gas is maximized by the claws of the two rotors. The rear stage exhaust is provided by a rear stage exhaust port that is communicated with the claws of the two rotors so as to exhaust the gas to the outside of the pump chamber including a step in which the compression ratio of the gas is maximized as compared with the previous stage. The front vent is closed by the rotor at the stage where the port is communicated to the outside of the pump chamber to maximize the compression ratio of the gas.

Further, according to one form of the claw pump according to the present invention, the front stage vent is provided on the one end wall portion, and the rear stage exhaust port is provided on the other end wall portion. can do.

Further, according to one form of the claw pump according to the present invention, the two rotors are arranged at one ends of the two rotating shafts and supported in a cantilevered state, and the one end wall portion is the two. It can be characterized in that it is located on the side of the bearing portion that supports one of the rotating shafts.

Further, according to one form of the claw pump according to the present invention, the front-stage vent and the rear-stage exhaust port overlap each other in a state in which they are overlapped with each other in the extension direction of the axis of the rotation shaft. It can be characterized in that it is provided in a divided form so as not to fit.

Further, according to one form of the claw pump according to the present invention, both are virtual in a state in which the front-stage vent and the rear-stage exhaust port are overlapped in the extension direction of the axis of the rotation shaft. It can be characterized in that it is provided in a form formed by dividing one of the exhaust side openings.

Further, according to one form of the claw pump according to the present invention, both are described in a state in which the front-stage vent and the rear-stage exhaust port are overlapped with each other in the extension direction of the axis of the rotation shaft. It can be characterized in that it is provided in a form in which a part of the rear exhaust port on the low compression ratio side overlaps.

Further, according to one form of the claw pump according to the present invention, the compression of both of the front-stage vent and the rear-stage exhaust port in a state of being overlapped in the extension direction of the axis of the rotation shaft. It can be characterized in that the boundary lines forming the rim on the side with the lower ratio are provided so as to overlap each other in the same shape.

Further, according to one form of the claw pump according to the present invention, the front-stage ventilation port and the rear-stage exhaust port are overlapped with each other in a state in which they are overlapped with each other in the extension direction of the axis of the rotation shaft. It is provided in a form divided so as not to fit, and both the front-stage ventilation port and the rear-stage exhaust port are provided on either the one end wall portion or the other end wall portion. Can be a feature.

Further, according to one form of the claw pump according to the present invention, the two rotors are arranged at one end of the two rotating shafts and supported in a cantilever state, and the front-stage vent and the rear-stage exhaust port are connected to each other. Both can be characterized in that they are provided on the other end wall portion located on the side opposite to the one end wall portion located on the side of the bearing portion that supports the two rotating shafts. ..

Further, according to one form of the claw pump according to the present invention, a pump chamber body portion provided by a cylinder portion and end wall portions provided on both end surfaces of the cylinder portion so as to form the pump chamber. , Between the two rotors and the body of the bearing, which is provided with a bearing that supports the two rotating shafts so that the two rotors are arranged at one end of the two rotating shafts and are supported in a cantilevered state. In addition, the pump body may be provided in a divided structure so as to form a cooling gap.

According to the claw pump according to the present invention, even when the vacuum pump is used in a high degree of vacuum, it is possible to prevent the pump chamber from being overheated and to significantly improve the pump efficiency, which is a special advantage. It has a great effect.

It is sectional drawing which shows the main part of the form example of the claw pump which concerns on this invention. It is a perspective view which shows the whole appearance of the form example of the claw pump which concerns on this invention. It is an exploded view which shows the main part of the form example of the claw pump which concerns on this invention. It is a perspective view which shows the form example of the member (cylinder case and side plate) which forms a pump chamber. It is a front view (a) of a side plate and a front view (b) of a cylinder case seen from the direction of the arrow A (see FIG. 4). It is a front view which shows the example of the form in which the exhaust side opening divided into the front-stage ventilation port (solid line) and the rear-stage exhaust port (dotted line) is overlapped in the axial direction of the rotation shaft. It is an operation diagram (state about three rotation positions of (a), (b), (c)) which shows the morphological example of the positional relationship between two rotors in rotation operation, a front-stage ventilation port and a rear-stage exhaust port. It is explanatory drawing which shows the form example of the division type of the exhaust side opening. It is explanatory drawing which shows the form example of the split type of the exhaust side opening. It is explanatory drawing which shows the form example of the overlap type of the exhaust side opening. It is explanatory drawing which shows the form example of the boundary matching type of the exhaust side opening. It is a perspective view which shows the form example which provided the divided exhaust side opening (front stage ventilation port and rear stage exhaust port) on one surface of a side plate. It is a side view which includes the cross section which shows the form example of the cooling air flow path of the claw pump which concerns on this invention. It is a perspective view which includes the cross section which shows the main part of the form example of the claw pump which concerns on this invention.

Hereinafter, a form example of the claw pump according to the present invention will be described in detail based on the attached drawings (FIGS. 1 to 7).

As shown in FIGS. 1 and 3, in the claw pump according to the present invention, the cylinder portion 10a is formed so as to form a pump chamber 10 (see FIG. 3 and the like) having a cross-sectional shape in which a part of two circles is overlapped. , One end wall portion 10b provided on one end face of the cylinder portion 10a, and the other end wall portion 10c provided on the other end face of the cylinder portion 10a.

Further, as shown in FIG. 3 and the like, the two

rotating shafts

20A and 20B are arranged in parallel in the pump chamber 10 and are provided so as to be rotated at the same speed in opposite directions. In this embodiment, the two

rotating shafts

20A and 20B are integrally fixed with gears 21A (drive side gear) and 21B (driven side gear), respectively. The pair of

gears

21A and 21B are meshed in a gear box 45 provided in the bearing portion body portion 200.

Further, as shown in FIG. 3 and the like, two

rotors

30A and 30B are provided in each of the two

rotating shafts

20A and 20B and arranged in the pump chamber 10, and are rotated and sucked in a non-contact state with each other. A hook-shaped claw is formed so that the gas can be compressed and exhausted.

Further, as shown in each figure, the exhaust side opening 50 is at least one of the one end wall portion 10b and the other end wall portion 10c, and the gas in the pump chamber 10 is compressed. It is provided with an opening at a position facing the site. As a result, a claw pump, which is a kind of biaxial rotary pump, is configured. Reference numeral 15 denotes an intake port, which is opened and provided at a position in the pump chamber 10 facing a portion where the gas is not compressed (in this embodiment, a wall portion forming the cylinder portion 10a).

Then, in the claw pump according to the present invention, the exhaust side opening 50 is communicated to the outside of the pump chamber 10 in the pre-stage where the compression ratio of the gas is maximized by the claws of the two

rotors

30A and 30B. A port 51 and a rear-stage exhaust port 52 communicated with each other so as to exhaust the gas to the outside of the pump chamber 10 including a step in which the compression ratio of the gas is maximized by the claws of the two

rotors

30A and 30B as compared with the previous stage. Is provided by. In this embodiment, the state of communicating with the outside of the pump chamber 10 is a state of communicating with and opening to the atmosphere, which is the outside air.

According to the claw pump according to the present invention, even when the vacuum pump is used in a high vacuum range where the ultimate vacuum is closer to the absolute vacuum, the pump chamber can be prevented from being overheated, and the pump can be used. The efficiency can be significantly improved. That is, the exhaust side opening 50 is composed of a front-stage ventilation port 51 and a rear-stage exhaust port 52 that are separately opened and provided. Therefore, when used at a high degree of vacuum, the unheated outside air is sucked into the front ventilation port 51, and the backflow of exhaust gas as in the conventional case can be reduced at the rear exhaust port 52, so that the pump chamber can be used. It is possible to prevent overheating.

That is, when the claw pump according to the present invention is used in a range where the degree of vacuum is higher than a certain level, the pressure may be negative even in the part where the inside of the pump chamber is compressed, and the pre-stage ventilation is performed. By opening the mouth 51, unheated outside air (for example, cooling air at atmospheric pressure at room temperature) can be taken in. Therefore, it is possible to prevent or suppress the backflow of the overheated gas (for example, air) at the post-stage exhaust port 52 which is opened later, and it is possible to suppress an increase in the internal temperature of the pump chamber. That is, the configuration including the front-stage vent 51 is the cooling secondary intake mechanism. In this way, cooling secondary intake is performed, and by taking in the outside air (cooling air) inside the pump chamber 10, the apparent amount of air (volume) is equivalent to the amount of backflow air, so the power changes. The internal temperature of the pump chamber 10 can be lowered without doing so. Therefore, overheating of the pump chamber 10 can be suppressed without impairing the energy saving property on the high vacuum side, which is an advantage of the claw pump, and the pump performance can be remarkably improved.

The vent that opens to the inside of the pump chamber 10 where compression is performed is the peripheral wall of the cylinder portion 10a so as to communicate with the outside in a situation where the compression ratio is low, which is the initial stage of the start of compression of the pump cycle. It is also conceivable to install it in a department or the like. However, if air is taken in through a vent that opens in such an early stage of compression, the amount of air processed may increase too much and power consumption may increase.

Further, in the examples shown in FIGS. 1 to 7, as shown in FIGS. 3 to 5, the pump chamber 10 is a cylinder case 11 in which a cylinder portion 10a and one end wall portion 10b are integrally provided. It is formed by a cylinder structure wall composed of a side plate 12 provided as the other end wall portion 10c. In this embodiment, the pump chamber 10 has a structure mainly composed of two members, but the present invention is not limited to this, for example, the cylinder portion 10a, one end wall portion 10b, and the other. Of course, it may be formed mainly by a member divided into three with the end wall portion 10c of the above.

Further, the present invention is not limited to the form in which the two

rotors

30A and 30B are bearing and supported in a cantilever state, and is also applied to a claw pump in which the

rotating shafts

20A and 20B are rotatably supported at both ends. It is configured so that it can be done.

Further, in this embodiment, as shown in FIGS. 1 to 7, the front-stage ventilation port 51 is provided on one end wall portion 10b, and the rear-stage exhaust port 52 is provided on the other end wall portion 10c. That is, both of the pair of

end wall portions

10b and 10c are provided with openings that communicate with the outside air (atmosphere in this embodiment) outside the pump chamber. According to this, the front-stage ventilation port 51 and the rear-stage exhaust port 52 can be reasonably and easily provided in an appropriate shape and at an appropriate position. Therefore, the degree of freedom in designing the claw pump corresponding to the required performance can be reasonably increased.

Next, a mechanism capable of preventing the pump chamber 10 from being overheated by the claw pump of the present embodiment will be described in detail below.
In a conventional claw pump, when the exhaust port is opened at a certain degree of vacuum or higher, the inside of the pump chamber is negative pressure, and backflow of exhaust (for example, atmospheric pressure air) is generated from the exhaust port. That is, in the conventional claw pump, the high temperature air (exhaust) inside the silent muffler connected to the exhaust port (the space including the exhaust pipe 55 (see FIG. 13)) may flow back from the exhaust port, and the pump It was a factor that caused the internal temperature of the room to rise. Therefore, conventionally, as a method of reducing the amount of backflow air, a method of increasing the compression ratio of the exhaust gas by the shape of the exhaust port has been used. That is, it has been designed so that the area of the exhaust port is made small and the exhaust port does not open unless the compression ratio of the exhaust becomes higher than a predetermined value. In this way, the higher the compression ratio is set, the more effective it is in preventing backflow, but when operating on the low vacuum degree side, the power rise becomes large, and the usable vacuum degree range is limited. That is, if the area of the exhaust port is reduced, the ventilation resistance of the exhaust becomes large when used in a low vacuum range, so that a large amount of power is required and the energy consumption increases.

On the other hand, in the claw pump of the present embodiment, when it is used in a range (for example, in the range of 60 to 95 kPa) where a predetermined high degree of vacuum is generated so that a negative pressure is generated even in a portion where the pump chamber 10 is compressed. In the cylinder case 11 (one end wall portion 10b) side cooling secondary intake port (pre-stage ventilation port 51), cooling secondary intake is performed, and the side plate 12 (the other end wall portion 10c) side exhaust port. The pump is exhausted from (post-stage exhaust port 52). That is, when the compression ratio of the front ventilation port 51, which is the opening on the one end wall portion 10b side, is equal to or lower than the compression ratio of the rear exhaust port 52, which is the opening of the other end wall portion 10c. It is provided in a shape that communicates with the outside.

According to the claw pump of this embodiment, when a predetermined high degree of vacuum (for example, 80 kPa or more) is generated, the pump chamber 10 has a compression ratio lower than the final compression ratio in a predetermined range. Negative pressure is maintained even at the site where internal compression is performed. At that stage, the front-stage vent 51 is opened to communicate with the outside air (for example, atmospheric pressure air), and cooling secondary intake air is performed. After that, the intake cooling air is added and compressed to the final compression ratio, and the air is exhausted from the rear exhaust port 52. That is, at the stage when the rear exhaust port 52 is opened and the final exhaust is performed, the cooling air is sucked in, so that the negative pressure in the compressed portion inside the pump chamber 10 is eliminated, and the subsequent exhaust is performed. In the process, backflow at the rear exhaust port 52 is prevented or suppressed. Therefore, it has been confirmed that overheating of the pump chamber 10 can be suppressed and a temperature rise of about 100 ° C. is suppressed in the examples, and the pump efficiency can be improved.

Hereinafter, with respect to the examples shown in FIGS. 1 to 6, the exhaust process capable of preventing overheating of the pump chamber 10 will be described in detail step by step based on FIG. 7.
At the stage of FIG. 7A, both the front ventilation port 51 and the rear exhaust port 52 are closed by one of the rotors 30A. That is, the large diameter regions of the main body of one of the rotors 30A are located in an overlapping state, and both the front ventilation port 51 and the rear exhaust port 52 are closed. Therefore, at this stage (section), neither exhaust nor intake is performed at the portion where the inside of the pump chamber 10 is compressed.

At the stage of FIG. 7B, the front ventilation port 51 is opened, and the rear exhaust port 52 is closed by one rotor 30A. That is, only the rear exhaust port 52 is blocked by the large diameter region of the main body of one of the rotors 30A.
The front-stage vent 51 of this embodiment is connected to a portion where the inside of the pump chamber 10 is compressed, and the compression ratio thereof is, for example, 2.0 to 2.4. Then, as described above, the front-stage vent 51 functions as a cooling secondary intake port into which the outside air is taken in when the portion of the pump chamber 10 where compression is performed has a negative pressure.

Further, the front-stage vent 51 of this embodiment is formed by a groove 51a (see FIG. 3 and the like) and a through hole 51b continuous with the groove 51a, and by opening even a part of the groove 51a, the through hole 51b It is shaped so that it can communicate with the outside through. That is, it is composed of a groove portion 51a provided within the plate thickness range of the member, and a through hole portion 51b formed by penetrating the groove portion 51a so as to communicate with the outside. The through hole portion 51b of this embodiment is provided in an L-shaped bent shape (see FIG. 1 and the like) so as to open downward to the outside. Further, the opening facing the outer side of the through hole portion 51b is formed in a circular shape, and for example, a pipe or the like may be connected as a connecting portion. Then, if a pipe as a continuous passage can be connected to the circular opening, the portion where the front ventilation port 51 is opened to the outside can be selectively moved to a position away from the rear exhaust port 52, and more. Can inhale gas such as low temperature air.

Further, the front-stage vent 51 functions as an exhaust port by being opened as shown in FIG. 7 (b) during operation at a low degree of vacuum. That is, until the inside of the pump chamber 10 has a predetermined high degree of vacuum, the part where the compression is performed inside the pump chamber 10 does not have a negative pressure, and in that situation, the compressed gas (for example, air) is released. , It will be exhausted from this front stage vent 51 as well. Therefore, at that time, the front-stage ventilation port 51 is a front-stage exhaust port. According to this, since the ventilation resistance of the exhaust gas can be reduced, the consumption of power can be suppressed.

At the stage of FIG. 7C, the rear exhaust port 52 is opened, and the front vent 51 is closed by one rotor 30A. That is, only the side of the front vent 51 is closed by the main body including the claw portion of one rotor 30A. Further, the small diameter region portion of the main body of one rotor 30A is positioned so that the one rotor 30A and the rear exhaust port 52 do not overlap each other, and the rear exhaust port 52 is in an open state. Then, in the portion where the inside of the pump chamber 10 communicating with the opened rear exhaust port 52 is compressed, the outside air is sucked and cooled by the front vent 51, and the compression ratio becomes high, so that the outside air becomes high. Since the pressure is higher than that of the above, the exhaust port 52 in the subsequent stage is properly exhausted without causing backflow. The latter-stage exhaust port 52 of this embodiment is connected to a portion where the inside of the pump chamber 10 is compressed and whose compression ratio is, for example, 2.4 or more or 3.0 or more.
According to this, as described above, the pump performance can be remarkably improved.

Further, in this embodiment, as shown in FIG. 3 and the like, two

rotors

30A and 30B are arranged at one end of two corresponding

rotating shafts

20A and 20B, respectively, and are supported in a cantilever state, and one end wall is provided. The portion 10b is located on the side of the bearing portion 40 that supports the two

rotating shafts

20A and 20B. This structure allows a simpler cantilevered claw pump with fewer parts to be properly configured.

FIG. 8 shows a first example of the exhaust side opening 50, which is a configuration adopted in the above-described morphological examples (see FIGS. 1 to 7), in order to make the morphological appearance easier to understand. In addition to being enlarged as compared with FIGS. 1 to 7, the opened space is described by hatching. That is, in this first example, the front-stage ventilation port 51 and the rear-stage exhaust port 52 are divided so as not to overlap each other in a state in which they are overlapped with each other in the extension direction of the axial centers of the

rotating shafts

20A and 20B. It is provided in the above-mentioned form. That is, the front-stage ventilation port 51 and the rear-stage exhaust port 52 are provided in a divided form by being arranged at a predetermined slight interval so that they do not overlap with each other. Therefore, in this case, as shown in FIG. 7B, the continuity of the exhaust side opening 50 formed by the front-stage ventilation port 51 and the rear-stage exhaust port 52 is momentarily interrupted.

FIG. 9 shows a second example of the exhaust side opening 50, in which the front ventilation port 51 and the rear exhaust port 52 are overlapped with each other in the extension direction of the axes of the

rotating shafts

20A and 20B. Both are provided in a form formed by dividing one virtual exhaust side opening 50. That is, the front-stage ventilation port 51 and the rear-stage exhaust port 52 are provided in a form in which one virtual exhaust side opening 50 is cut out, so that the first-stage ventilation port 51 and the rear-stage exhaust port 52 are formed in a divided manner.

FIG. 10 shows a third example of the exhaust side opening 50, in which the front ventilation port 51 and the rear exhaust port 52 are overlapped with each other in the extension direction of the axial centers of the

rotating shafts

20A and 20B. Both are provided so as to overlap each other on a part of the rear exhaust port 52 on the lower compression ratio side.

FIG. 11 shows a fourth example of the exhaust side opening 50, in which the front vent 51 and the rear exhaust 52 are overlapped with each other in the extension direction of the axes of the

rotating shafts

20A and 20B. The boundary line 50a forming the rim on the side where the compression ratio of both is low is provided so as to overlap each other in the same shape.

In the above example of the form of the exhaust side opening 50, the smaller the opening area of the rear exhaust port 52 is, the more the performance of the claw pump that generates a high degree of vacuum can be improved. Further, the larger the opening area of the front-stage ventilation port 51 and the rear-stage exhaust port 52 is formed, the better the performance of the claw pump that processes a larger air volume can be improved.

Further, in the present invention, as shown in FIG. 12, both of the front-stage vents 51 and the rear-stage exhaust ports 52 are viewed as being overlapped with each other in the extension direction of the axial centers of the

rotating shafts

20A and 20B. The two

rotors

30A and 30B are provided at one ends of the two

rotating shafts

20A and 20B and are supported in a cantilevered state by being provided in a form in which they are separated so as not to overlap each other. Both of these are provided on the other end wall portion 10c located on the side opposite to the one end wall portion 10b located on the side of the bearing portion 40 that supports the two

rotating shafts

20A and 20B. You can also do it.

According to this, the front-stage ventilation port 51 and the rear-stage exhaust port 52 can be rationally arranged only on one surface of the end wall portion, and the optimum form can be obtained according to the usage conditions. The degree of freedom in design can be increased, including the relationship with the device. That is, since there is a predetermined distance between the front-stage ventilation port 51 and the rear-stage exhaust port 52, both can be separated, and as shown in FIG. 12, the opening of the front-stage ventilation port 51 to the outside and the rear-stage exhaust port 52 It can be separated from the opening to the outside (the opening provided via the exhaust pipe 55). Therefore, the front-stage vent 51 can take in unheated gas, and as described above, the performance of the claw pump can be improved.

The claw pump of the present invention is not limited to the above-mentioned form, and both the front-stage vent 51 and the rear-stage exhaust port 52 are arranged only on one end wall portion 10b, the front-stage vent 51 and the rear-stage exhaust. Both of the ports 52 are arranged on both the one end wall portion 10b and the other end wall portion 10c, the front stage vent 51 is arranged on both end wall portions, and the rear stage exhaust port 52 is arranged on one end. It is also possible to use either a form in which the front ventilation port 51 is arranged on one end wall portion or a form in which the rear exhaust port 52 is arranged on both end wall portions. These forms may be appropriately and selectively adopted according to various usage conditions. When both end walls of the front ventilation port 51 and the rear exhaust port 52 are arranged, the size, shape, or combination thereof may be appropriately and selectively designed according to the usage conditions, and have the same form. Of course, there is no need.

Next, a cooling mode related to the exterior of the claw pump of this embodiment will be described with reference to FIGS. 13 and 14.
Reference numeral 100 denotes a pump chamber body portion, and the pump chamber body portion 100 is provided by

end wall portions

10b and 10c provided on each of the cylinder portion 10a and both end faces of the cylinder portion 10a so as to form the pump chamber 10. Has been done.

Reference numeral 200 denotes a bearing portion body portion. In the bearing portion body portion 200, two rotors 30A (driving side rotor) and 30B (driven rotor) have two rotating shafts 20A (driving side rotating shaft) and 20B (driven). A bearing portion 40 that supports the

rotating shafts

20A and 20B is provided so as to be arranged at one end of the side rotating shaft) and supported in a cantilevered state. The pump main body is composed of the bearing portion body portion 200 and the pump chamber body portion 100.

The claw pump according to the present invention has a pump chamber body portion 100 and a bearing portion body portion so that a cooling gap 60 is formed between the pump chamber body portion 100 and the bearing portion body portion 200. The pump body is provided in a structure divided into 200 and 200.

According to the rotary pump according to the present invention, it is possible to reduce the heat generated by driving from being transmitted to the bearing portion body portion 200, and to achieve a special advantageous effect that the functional parts constituting the bearing portion 40 and the like can be extended in life. .. That is, according to the present invention, heat conduction can be minimized by dividing the pump chamber body portion 100 and the bearing portion body portion 200. Further, by flowing cooling air between the pump chamber body portion 100 and the bearing portion body portion 200, heat transfer can be suppressed and cooling by heat dissipation can be promoted. As a result, the temperature rise of the bearing portion body portion 200 can be suppressed, and the life of the functional component can be extended.

Note that the functional parts are constituent members including the bearing 41 and the oil seal 42, and are treated as consumable parts. By extending the life of these functional parts, running costs can be reduced.

Further, in the present embodiment, as shown in FIGS. 1 and 2, the columnar connecting portion 101 for connecting so that both the portion of the pump chamber body portion 100 and the portion of the bearing portion body 200 are paired with each other. 201 (see FIGS. 1 to 3) is provided. For this connection, four pairs of columnar connecting

portions

101 and 201 are provided, and in this embodiment, as is clear from FIG. 3 and the like, the

columnar connecting portions

101 and 201 are arranged at the four corners of the body. ing. According to this, the pump chamber body portion 100 and the bearing portion body portion 200 can be stably connected. The fastening means for connecting in this embodiment is a screw connection using bolts. By the way, the present invention is not limited to the present embodiment, and the form of the portion where the cooling gap 60 is formed may be formed in an integral structure. For example, in the case of manufacturing by casting molding, the cooling gap 60 may be formed by the core.

Further, in this embodiment, cooling air (see the arrow in FIG. 13) is generated in the coupling portion 73 (see FIG. 2) that connects the other end of the rotating shaft 20A and the drive shaft 71 of the drive motor 70. The blower blades 75 are integrally fixed and arranged, and as shown in FIG. 13, the cooling air generated by the rotation of the blower blades 75 flows on the surface of the pump chamber body 100 to cool the pump chamber 10. As such, a blower guide unit 80 for guiding the flow of the cooling air is provided. According to this, the cooling air can be efficiently applied to the surface of the pump chamber body 100, and the cooling performance can be improved.

Further, in the example of the present embodiment, the cooling air is blown upward from the lower side of the pump chamber body portion 100 to the blower guide portion 80 to cover the surfaces of both

end wall portions

10b and 10c of the pump chamber body portion 100. A bottom air passage 81 is formed as a passage on the lower side of the bearing portion body portion 200 and the pump chamber body portion 100 so as to flow, and guides the flow of the cooling air.

According to this, both

end wall portions

10b and 10c of the pump chamber body portion 100 can be cooled at the same time, and the exhaust pipe 55 can also be cooled, so that the cooling can be performed efficiently. In addition, a rational flow path that does not raise dust on the floor of the cooling air can be appropriately configured.

Further, as shown in FIG. 13, the blower guide portion 80 of this embodiment is a coupling portion 73 (in which the pump chamber body portion 100, the bearing portion body portion 200, and the blower blade 75 are integrally fixed and arranged. It is composed of a box-shaped cover 90 formed of a plate-shaped member so as to cover the entire surface (see FIG. 2). That is, a suction port 91 for introducing cooling air is provided in the vicinity of the blower blade 75 of the box-shaped cover 90, and the cooling air discharged from the blower blade 75 is directed in the direction of the bearing portion body portion 200 and the pump chamber. The bottom air passage 81 that guides the flow of the cooling air is provided in a form that is bulged downward by a plate-shaped member (a form in which the cross section of the flow path is wide) so as to be smoothly directed to the side of the body portion 100. There is. Then, in order to improve the cooling performance by increasing the flow velocity of the cooling air flow through the surfaces of both

end wall portions

10b and 10c of the pump chamber body portion 100, the flow path of the bottom blower passage 81 is the pump chamber. The shape is narrowed as it approaches the body portion 100 (the cross section of the flow path is narrow). Then, the discharge port 92 and the discharge port are placed on the upper part of the box-shaped cover 90 so that the cooling air that has passed through the surfaces of both

end wall portions

10b and 10c of the pump chamber body portion 100 can be smoothly blown from the lower side to the upper side. 93 is provided. The suction port 91, the discharge port 92, and the discharge port 93 of this embodiment are provided in a louver shape.

According to the cooling structure explained above, the claw pump can be reasonably and appropriately configured, and the cooling performance can be improved. Further, in the claw pump according to the present invention, the lower side of the pump chamber 10 is likely to overheat, and a structure in which cooling air is applied from the lower side can be appropriately formed as described above. Therefore, the pump chamber 10 can be efficiently cooled, the pump performance can be improved, and the life of the functional component can be extended, which is a special advantageous effect.

Further, since the front-stage vent 51 is provided below the rotating

shafts

20A and 20B, it becomes easy to suck in the cooling air that has not been heated yet, and the inside of the pump chamber 10 can be efficiently cooled. Therefore, the pump performance can be improved.

Further, in this embodiment, as shown in FIGS. 3 and 4, the surface of one end wall portion 10b forming the cooling gap 60 and the wall portion forming the bearing portion 40 facing the end wall portion 10b is used for cooling.

Ribs

17 and 47 are provided. These cooling

ribs

17 and 47 are provided in a form extending in the vertical direction, and can guide the cooling air flowing from the bottom to the top without obstructing the flow, and can improve the cooling efficiency.

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

10 Pump chamber 10a Cylinder part 10b One end wall part 10c The other end wall part 11 Cylinder case 12 Side plate 15 Intake port 17 Cooling rib 20A Rotation shaft (drive side rotation shaft)
20B rotating shaft (driven side rotating shaft)
21A gear (drive side gear)
21B gear (driven gear)
30A rotor (drive side rotor)
30B rotor (driven rotor)
40 Bearing 41 Bearing 42 Oil seal 45 Gear box 47 Cooling rib 50 Exhaust side opening 50a Boundary line forming the rim on the side with a low compression ratio 51 Front vent 51a Groove 51b Through hole 52 Rear exhaust 55 Exhaust Piping 60 Cooling gap 70 Drive motor 73 Coupling part 75 Blower blade 80 Blower guide part 81 Bottom air passage 90 Box-shaped cover 91 Suction port 92 Outlet port 93 Outlet port 100 Pump room body part 101 Columnar connection part 200 Bearing part body Part 201 Columnar connection part

Claims

On the cylinder portion, one end wall portion provided on one end face of the cylinder portion, and the other end face of the cylinder portion so as to form a pump chamber having a cross-sectional shape in which a part of two circles is overlapped. With the other end wall provided
Two rotating shafts arranged in parallel in the pump chamber and rotated in opposite directions at the same speed,
Two rotors provided in each of the two rotating shafts and arranged in the pump chamber, and having hook-shaped claws formed so that the inhaled gas can be compressed and exhausted by rotating in a non-contact state with each other. When,
An exhaust side opening provided at least one of the one end wall portion and the other end wall portion at a position facing the portion where the gas is compressed in the pump chamber. It is a claw pump equipped with
The exhaust side opening communicates with the outside of the pump chamber in the pre-stage where the compression ratio of the gas is maximized by the claws of the two rotors, and the claws of the two rotors communicate with each other. It is provided by a rear stage exhaust port that communicates with the outside of the pump chamber so as to exhaust the gas to the outside including the stage where the compression ratio of the gas is maximized as compared with the previous stage.
A claw pump characterized in that the front-stage exhaust port is provided so as to be closed by the rotor at a stage where the rear-stage exhaust port is communicated with the outside of the pump chamber to maximize the compression ratio of gas.
The claw pump according to claim 1, wherein the front-stage vent is provided on the one end wall portion, and the rear-stage exhaust port is provided on the other end wall portion.
Regarding the form in which the front-stage vent and the rear-stage exhaust port are overlapped in the extension direction of the axis of the rotation shaft, they are provided in a separated form so as not to overlap each other. The claw pump according to claim 2, wherein the claw pump is characterized.
The front-stage ventilation port and the rear-stage exhaust port are formed by dividing one virtual exhaust-side opening in a state in which the front-stage ventilation port and the rear-stage exhaust port are overlapped with each other in the extension direction of the axis of the rotation shaft. The claw pump according to claim 2, wherein the claw pump is provided in a form.
Regarding the form in which the front-stage vent and the rear-stage exhaust port are overlapped in the extension direction of the axis of the rotation shaft, both are overlapped at a part of the rear-stage exhaust port on the lower compression ratio side. The claw pump according to claim 2, wherein the claw pump is provided in.
Regarding the form in which the front-stage vent and the rear-stage exhaust port are overlapped with each other in the extension direction of the axis of the rotation shaft, the boundary lines forming the rim on the side where the compression ratio of both is low are matched. The claw pump according to claim 2, wherein the claw pump is provided in a form that overlaps with each other.
The two rotors are arranged at one end of each of the two rotating shafts and supported in a cantilevered state, and the one end wall portion is located on the side of the bearing portion that supports the two rotating shafts. The claw pump according to any one of claims 1 to 6.
The front-stage ventilation port and the rear-stage exhaust port are provided in a form in which the front-stage ventilation port and the rear-stage exhaust port are divided so as not to overlap each other in a state in which they are overlapped with each other in the extension direction of the axis of the rotation shaft. The claw pump according to claim 1, wherein both the port and the rear exhaust port are provided on either the one end wall portion or the other end wall portion.
The two rotors are arranged at one end of the two rotating shafts and supported in a cantilevered state, and both the front vent and the rear exhaust port are on the side of the bearing portion that supports the two rotating shafts. The claw pump according to claim 8, wherein the claw pump is provided on the other end wall portion located on the opposite side of the one end wall portion located in.
A pump chamber body portion provided by a cylinder portion and end wall portions provided on both end faces of the cylinder portion so as to form the pump chamber, and the two rotors are one end of the two rotating shafts. The pump body is provided with a bearing portion that supports the two rotating shafts so as to be supported in a cantilevered state. The claw pump according to any one of claims 1 to 9, wherein the claw pump is provided in a divided structure.