JP2007077813A - Pump assembling method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a method for assembling an efficient pump by suppressing leakage of compressed high pressure operating fluid from an assembling clearance between a member covering a rotor arranged in a cylinder and a rotating rotor, and simultaneously preventing failure such as seizure caused by the rotor being brought into contact with the member covering the rotor, and to provide a pump assembling method capable of maintaining stable performance in further miniaturization of, especially a compact pump of oilless system. <P>SOLUTION: In the pump assembling method of the prevent invention, the end part of the rotor is assembled to be previously brought into contact with the member covering the rotor, and under this condition, the rotor is forcibly rotated, thereby the end part of the rotor is slid upon the member covering the rotor, and the shapes of both the members to be brought into contact with each other are assembled by mutually fitting by sliding action. By this operation, the clearance between the member covering the rotor and the end part of the rotor is removed or minimized. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a pump used in an air conditioner or a portable computer.

  In this type of so-called vane type rotary pump, when the rotor rotates, the vane moves slidably in a vane groove disposed in the rotor, and the end of the vane is pushed against the inner peripheral surface of the cylinder by the action of centrifugal force. By being applied, the sealing property between the vane and the inner peripheral surface of the cylinder is ensured. A plurality of pump chambers are configured by partitioning the inner space of the cylinder and the rotor with vanes, and the volume of each pump chamber is continuously expanded and contracted as the rotor rotates. Pump action occurs.

  At this time, it was compressed from the high pressure side pump chamber in the compression process to the low pressure side pump chamber in the suction and expansion processes through the gap between the rotor covering the rotor disposed on the end face of the cylinder and the rotor. Since the high-pressure fluid leaks, if this gap is large, the efficiency of the pumping operation is significantly reduced.

  On the other hand, if this gap is too small, each part, including the rotor that rotates due to the heat generated by the pump drive, will change in expansion compared to when it is cold, so this gap will gradually become smaller over time and will eventually cover the rotor. When the rotor contacts the member, a failure such as seizure occurs, and the rotation of the rotor stops and the pump function is hindered.

  For this reason, the gap is made as small as possible within a limit that does not greatly impede the pump function, but there is a problem that the improvement of the pump efficiency is hindered as a result.

  In particular, in the case of a pump with a small pump chamber volume, the ratio of the amount of leakage from the gap to the pump chamber volume tends to be relatively large compared to a pump with a large pump chamber volume. It was a big obstacle to improve the performance of the pump.

As means for solving the conventional problem of reducing the clearance, a method of finely adjusting the clearance between the side surface of the rotating rotor and the inner peripheral surface of the cylinder by using a spring and an adjusting screw (for example, see Reference 1), rotation A non-metallic dissimilar substance is inserted and arranged between the rotor and the cylinder to reduce the clearance (for example, see Reference 2), or a self-lubricating seal member is provided on the sliding portion of the oil-free rotary pump. Methods have been devised to eliminate gaps by using them (see, for example, References 3 and 4).
JP-A-8-121353 Japanese Patent Laid-Open No. 10-252683 JP-A-8-021389 JP-A-8-021388

  An object of the present invention is to improve the efficiency of the pump by suppressing the compressed high-pressure fluid from leaking from the gap between the rotating rotor and the member covering the rotor. Thus, a pump assembly method capable of maintaining stable performance when the pump is reduced in size is provided.

  In order to solve the above-described problem, in the pump assembly method of the present invention, the member covering the rotor is assembled in advance so that the end of the rotor is in contact with the member covering the rotor, and the rotor is forcibly rotated in this state to form the member covering the rotor. By sliding the end of the rotor so that the shapes of the sliding parts of both members that come into contact with each other are assembled, the gap between the member that covers the rotor and the rotor end is eliminated or extremely small. Is realized.

  Furthermore, the contact area of the member of the sliding part can be reduced by forming the shape of the part where the member that covers the rotor end and the member that contacts the rotor into a substantially convex shape, or a member that is relatively softer than the sliding counterpart member. By arranging it, it is devised so that the shapes can be easily adapted to each other.

  By the above means, when the pump is driven, it is possible to prevent the rotor from contacting the member covering the rotor and causing a failure such as seizure in advance, and the assembly gap in the part where both members face each other is set to be extremely small or extremely small. The amount of leakage of the compressed high pressure fluid can be suppressed extremely low.

  In the pump assembly method of the present invention, since the high-pressure fluid compressed in the high-pressure side pump chamber is greatly suppressed from leaking out to the low-pressure side pump chamber in the suction and expansion processes, the pump action is improved as compared with the conventional method. Efficiency is improved and a pump with stable performance can be provided.

  In particular, the present invention provides a pump assembling method capable of maintaining stable performance for further miniaturization of an oil-free small pump.

  In the first aspect of the invention, a cylinder and a rotating rotor are provided in the cylinder, and a groove is provided in the rotating rotor, and the vane is disposed in the groove so as to be slidable as the rotor rotates. On the other hand, in a pump in which a member that covers the rotor is disposed on the end surface of the cylinder, the rotor is forcibly rotated after assembling the member that covers the rotor so that the end of the rotor that is disposed opposite to the member is contacted in advance. By sliding the end portion of the rotor on the member covering the rotor, the shapes of the sliding portions of the two members in contact with each other are assembled to each other.

  With this feature, the rotor that rotates during actual operation of the pump does not have to worry about seizure or other malfunctions, but the high-pressure side pump chamber is greatly prevented from leaking into the low-pressure side pump chamber. Therefore, the efficiency of the pump action is improved as compared with the conventional one.

  According to a second aspect of the present invention, the shape of the end portion of the rotor disposed opposite to the member covering the rotor is made substantially convex, and the rotor is forcedly rotated after assembling so as to contact the member covering the rotor in advance. The substantially convex shape part of the said rotor edge part is slid on the member to cover, and the shape of the sliding part of both members is mutually adjusted and assembled.

  With this feature, the rotor that rotates during actual operation of the pump does not have to worry about seizure or other malfunctions, but the high-pressure side pump chamber is greatly prevented from leaking into the low-pressure side pump chamber. Therefore, the efficiency of the pump action is improved as compared with the conventional one.

  According to a third aspect of the present invention, a member covering the rotor is formed with a substantially convex raised portion with respect to the rotation center of the rotor at a portion where the rotor end portion is opposed, so that the end portion of the rotor comes into contact with this in advance. After assembling, the rotor is forcedly rotated, and the rotor end is slid into the roughly convex portion provided on the member that covers the rotor, so that the shapes of the sliding portions of both members are adjusted to each other. .

  With this feature, the rotor that rotates during actual operation of the pump does not have to worry about seizure or other malfunctions, but the high-pressure side pump chamber is greatly prevented from leaking into the low-pressure side pump chamber. Therefore, the efficiency of the pump action is improved as compared with the conventional one.

  According to a fourth aspect of the present invention, a member that is relatively softer than the member that covers the rotor is disposed on a part of the rotor end that is disposed opposite to the member that covers the rotor, and this covers the rotor in advance. After assembling to contact the member, the rotor is forcibly rotated to slide the soft member on the member covering the rotor so that the shapes of the sliding portions of both members are adjusted to each other.

  With this feature, the rotor that rotates during actual operation of the pump does not have to worry about seizure or other malfunctions, but the high-pressure side pump chamber is greatly prevented from leaking into the low-pressure side pump chamber. Therefore, the efficiency of the pump action is improved as compared with the conventional one.

  According to a fifth aspect of the present invention, a member that covers the rotor is disposed so that a member that is relatively softer than the rotor has a substantially convex shape with respect to the rotation center of the rotor at a portion where the end of the rotor is opposed. After being assembled so as to contact the end of the rotor in advance, the rotor is forcibly rotated to slide the end of the rotor on the soft member so that the shapes of the sliding portions of both members are adjusted to each other. .

  With this feature, the rotor that rotates during actual operation of the pump does not have to worry about seizure or other malfunctions, but the high-pressure side pump chamber is greatly prevented from leaking into the low-pressure side pump chamber. Therefore, the efficiency of the pump action is improved as compared with the conventional one.

  According to a sixth aspect of the present invention, a substantially annular partition is disposed at the end of the rotor facing the member covering the rotor so as to be substantially concentric with the rotation center of the rotor. After assembling to contact the covering member, the rotor is forcibly rotated so that the annular partition is slid on the member covering the rotor and the shapes of the sliding parts of both members are adjusted to each other. Yes.

  With this feature, the rotor that rotates during actual operation of the pump does not have to worry about seizure or other malfunctions, but the high-pressure side pump chamber is greatly prevented from leaking into the low-pressure side pump chamber. Therefore, the efficiency of the pump action is improved as compared with the conventional one.

(Embodiment 1)
Examples of the first and second aspects of the invention are shown in FIGS.

  FIG. 1 is a plan view showing the internal structure of the pump of the present invention, and FIG. 2 shows a cross section A-O-A of FIG. For comparison, a conventional pump is illustrated in FIGS. 12 and 13.

  FIGS. 1 and 2 and FIGS. 12 and 13 of the conventional example show the configuration of the pump taking the case of three vanes as an example.

  First, the prior art will be described with reference to FIGS. In these figures, a rotor 20 is disposed inside the cylinder 1 and rotates inside the cylinder about the drive shaft 5.

On the other hand, the rotor 20 is provided with vane grooves 6a, 6b, and 6c, and the vanes 3a, 3b, and 3c are slidably disposed in the grooves. When the rotor 20 rotates, the vane rotates along the inner peripheral surface of the cylinder 1 by the action of centrifugal force as shown in the figure. At this time, the space formed by the rotor 20 and the cylinder 1 is partitioned into a plurality by vanes, and the rotor and the vanes are covered by the members 40a and 40b covering the rotor disposed on the upper and lower end surfaces of the cylinder. Chambers 7a, 7b, 7c are configured. In addition, illustration of the inlet port, discharge port, etc. of a pump is abbreviate | omitted in the figure.

  In order to enable high-speed rotation of the rotor 20 in the pump, a gap is always required between the members 40a and 40b covering the rotor and the rotor 20, but this gap is a so-called assembly gap, and the size thereof is the cylinder 1. , The amount of each component is selected and combined based on the measured values of the dimensions of the finished products of the rotor 20 and the vanes 3a, 3b, and 3c.

  And the smaller the size of this gap, the smaller the leakage of compressed fluid from the high pressure side pump chamber, so the flow rate characteristics of the pump will improve, but on the other hand, due to the heat generated by the operation of the pump, When dimensional changes due to thermal expansion occur and these dimensional changes are collected and the gap becomes zero, the rotation of the rotor 20 becomes a so-called locked state and the pump function stops.

  If the gap is increased to avoid this, loss due to leakage of the compressed fluid increases and the flow rate characteristic of the pump is remarkably deteriorated. If the rotational speed of the rotor 20 is increased to compensate for this decrease in the flow rate characteristic, the input value also increases. As a result, the energy efficiency deteriorates, and a part of the input energy finally contributes to heat generation. The dimensional change of each part selected and combined by this heat also becomes large, and finally the rotating rotor 20 and the rotor This creates a vicious circle in which the gaps between the members 40a and 40b covering the surface act in the direction of decreasing.

  For this reason, in the prior art, it is necessary to keep the size of the gap at a reasonable size that is not too small and not too large considering the amount of heat generated when the pump is driven. Accordingly, the rotor 20 maintains the balance of the gap in the above-described vicious circle environment in which the flow rate characteristic is reduced due to the leakage of the compressed fluid from the gap and the input is increased due to the high-speed rotation of the rotor 20 to compensate for this. The only possible response was to obtain an inefficient pump while avoiding the possibility that the rotation of the motor would lock.

  On the other hand, in the present invention, as shown in FIGS. 1 and 2, the end portions of the rotor 21 facing the members 40a and 40b (not shown in FIGS. 1 and 2) covering the rotor are respectively pump chambers 7a and 7b. , 7c is formed in a generally convex shape so as to cut off the communication, and this part is assembled in a state of being in contact with a member covering the rotor in advance. Then, by forcibly driving the drive shaft 5 from the outside of the pump, the rotor 21 rotates while contacting and sliding with the members 40a and 40b covering the rotor, so that the contact between the rotor 21 and the members 40a and 40b covering the rotor is achieved. The shapes of the parts become compatible with each other by the sliding action. As a result, the gap between the rotor 21 and the members 40a and 40b covering the rotor is eliminated or extremely reduced, but the sliding resistance is already removed during forced driving even when the pump is driven by itself. Therefore, troubles such as seizure do not occur during actual operation of the pump.

  In addition, when it is desired to accurately eliminate the effects of thermal expansion due to the temperature rise of pump components during actual operation of the pump, the rotor is preliminarily set in a temperature atmosphere set based on the member temperature assumed during actual operation of the pump. Can be forcibly driven.

  Due to the above features, there is no fear of seizure or the like caused by the rotating rotor 21 during actual operation of the pump, while compressed high-pressure fluid leaks from the high-pressure side pump chamber to the low-pressure side pump chamber. Since it is suppressed from taking out, the efficiency of the pumping action is improved as compared with the conventional case.

  In FIG. 2, in order to facilitate understanding of the relationship of the assembly gap between the rotor and the member covering the rotor, the shape of the rotor end is exaggerated in the size of the gap.

(Embodiment 2)
FIG. 3 is a plan view of the first and third examples of the pump according to the present invention, FIG. 4 is a cross-sectional view taken along the line B-O-B of FIG. 3, and FIG. 4 is a plan view of a member covering the rotor of FIG. 5 shows.

  In the present embodiment, as shown in FIGS. 4 and 5, the members 42a and 42b (42b not shown) covering the rotor 22 are roughly projected so as to block the communication between the pump chambers 7a, 7b and 7c. On the surface facing the rotor 22, the raised portion is shaped at a position that is concentric with the rotation center of the rotor 22.

  And it is assembled in the state which this protrusion-shaped part contacted the rotor previously. By forcibly driving the drive shaft 5 from the outside of the pump, the rotor 22 rotates while contacting and sliding with the members 42a and 42b covering the rotor, so that the contact between the rotor 22 and the members 42a and 42b covering the rotor is achieved. The shapes of the parts become compatible with each other by the sliding action. As a result, the gap between the rotor 22 and the members 42a and 42b covering the rotor is eliminated or extremely reduced, but the sliding resistance is already removed during forced driving even when the pump is driven by itself. Therefore, troubles such as seizure do not occur during actual operation of the pump.

  Further, when it is desired to accurately eliminate the influence of thermal expansion due to the temperature rise of the pump constituent members during actual operation of the pump, it may be handled in the same manner as in the first embodiment.

  Due to the above features, there is no fear of seizure such as seizure due to the rotating rotor 22 during actual operation of the pump, while compressed high pressure fluid leaks from the high pressure side pump chamber toward the low pressure side pump chamber. Therefore, the efficiency of the pumping action is improved as compared with the conventional case.

  In FIG. 4, in order to advance the understanding of the relationship of the assembly gap between the rotor and the member covering the rotor, the member disposed around the rotor and the rotor and the member covering the rotor Regarding the shape, the size of the gap is exaggerated.

(Embodiment 3)
Examples of the first invention, the second invention, and the fourth invention of the pump according to the present invention are shown in FIGS. 6 is a plan view of the present invention, and FIG. 7 shows a cross section C—O—C of FIG.

  In the present embodiment, as shown in FIGS. 6 and 7, the shielding member 8 is provided at each pump portion at a portion where the rotor 23 faces the members 40a and 40b (not shown in FIGS. 6 and 7) covering the rotor. The chambers 7a, 7b and 7c are arranged so as to block communication. The shielding member 8 is made of a material that is relatively softer than the members 40 a and 40 b that cover the rotor, and is shaped so as to have a generally protruding shape with respect to the end of the rotor 23.

  The pump is assembled in a state where the shielding member 8 is in contact with the members 40a and 40b covering the rotor in advance. By forcibly driving the drive shaft 5 from the outside of the pump, the shielding member 8 disposed on the rotor 23 rotates while contacting and sliding with the members 40a and 40b covering the rotor. The shape of the contact portion with the members 40a and 40b covering the surface becomes compatible with each other by the sliding action. As a result, the clearance between the rotor 23 and the members 40a and 40b covering the rotor via the shielding member 8 is eliminated or extremely reduced, but the sliding resistance is already forced even when the pump is driven by itself. Since it is removed during driving, troubles such as seizure do not occur during actual operation of the pump.

  Further, when it is desired to accurately eliminate the influence of thermal expansion due to the temperature rise of the pump constituent members during actual operation of the pump, it may be handled in the same manner as in the first embodiment.

Due to the above characteristics, there is no fear of failure such as seizure due to the rotating rotor 23 or the shielding member 8 during actual operation of the pump, while the compressed high pressure fluid is directed from the high pressure side pump chamber toward the low pressure side pump chamber. As a result, the pumping efficiency is improved as compared with the conventional case.

  In FIG. 7, in order to advance the understanding of the relationship of the assembly gap between the rotor and the member covering the rotor, the shape of the portion of the rotor and the member disposed around the rotor facing the member covering the rotor is a gap. The figure is exaggerated in size.

(Embodiment 4)
Examples of the first invention, the third invention and the fifth invention of the pump according to the present invention are shown in FIGS. 8 is a plan view of the pump, and FIG. 9 shows a cross section D-O-D of FIG.

  In the present embodiment, as shown in FIGS. 8 and 9, the shielding member 9 is provided in each pump chamber 7a, in a portion where members 44a and 44b (44b not shown) covering the rotor face the rotor 24, as shown in FIGS. 7b and 7c are arranged to block communication. The shielding member 9 is made of a material that is relatively softer than the rotor 24, and is shaped so as to have a generally protruding shape with respect to the ends of the members 44a and 44b covering the rotor.

  The pump is assembled with the shielding member 9 in contact with the rotor 24 in advance. Then, by forcibly driving the drive shaft 5 from the outside of the pump, the shielding member 9 disposed on the members 44a and 44b covering the rotor rotates while contacting and sliding with the rotor 24. Therefore, the shielding member 9 and the rotor The shape of the contact surface becomes compatible with each other by the sliding action. As a result, the gap between the members 44a and 44b covering the rotor via the shielding member 9 and the rotor 24 is eliminated or extremely reduced, but the sliding resistance is already forced even when the pump is driven by itself. Since it is removed during driving, troubles such as seizure do not occur during actual operation of the pump.

  Further, when it is desired to accurately eliminate the influence of thermal expansion due to the temperature rise of the pump constituent members during actual operation of the pump, it may be handled in the same manner as in the first embodiment.

  Due to the above-described features, there is no risk of seizure such as seizure due to the rotating rotor 24 and the shielding member 9 during actual operation of the pump, while the compressed high-pressure fluid is directed from the high-pressure side pump chamber toward the low-pressure side pump chamber. As a result, the efficiency of the pumping action is improved as compared with the conventional case.

  In FIG. 9, in order to facilitate understanding of the relationship of the assembly gap between the rotor and the member covering the rotor, the shape of the portion where the member covering the rotor and the shielding member face the rotor and the members disposed around the rotor Is shown exaggerating the size of the gap.

(Embodiment 5)
FIG. 10 shows a plan view of the first and sixth examples of the pump according to the present invention, and FIG. 11 shows a partial cross-sectional view of FIG.

  In order to advance understanding of the relationship between the assembly gaps in the examples shown in FIGS. 10 and 11 as well, in FIG. 11, the shape of the gap between the rotor and the member disposed around the rotor and the member that covers the rotor is not shown. The size is exaggerated.

10 and 11, partition walls 10a, 10b, and 10c are arranged in concentric rings on the end of the rotor 25 with respect to the drive shaft 5, respectively. Are slightly in contact with the members 40a and 40b (not shown in FIGS. 10 and 11). Accordingly, the pump chambers 7a, 7b, and 7c are shielded from communicating with each other at the partition wall, and the sealing effect can be maintained so that the compressed fluid does not leak between the pump chambers. In this state, when the drive shaft 5 is subjected to an aging operation by using external power or by the self-driving of the pump, the partition wall is disposed in a substantially concentric ring shape with respect to the drive center. The shape of the portion in contact with the covering member is quickly adapted to the sliding action, and the amount of wear generated is also suppressed. The abrasion powder generated at this time from the member that covers the partition wall and the rotor is discharged together with the working fluid in advance by the pump action, so that the rotor 25 and the partition walls 10a, 10b, and 10c rotate during actual operation of the pump after aging. It does not become resistance to.

  Due to the above features, there is no risk of malfunction such as seizure of the rotating rotor and bulkhead during actual operation of the pump. On the other hand, compression and high pressure are performed from the high pressure side pump chamber to the low pressure side pump chamber. Since the leakage of fluid is extremely suppressed, the efficiency of the pumping action is improved as compared with the conventional case.

  As described above, in the pump assembling method according to the present invention, the assembly gap between the rotor and the member covering the rotor is physically sealed. For this reason, since the leakage of the compressed high-pressure working fluid that has been communicated from the high-pressure side pump chamber to the low-pressure side pump chamber through this gap is cut off, the efficiency of the pumping action is improved compared to the conventional case, and the performance Stable pump can be provided.

  In the case where downsizing is indispensable, such as an air conditioner for air conditioning, a small pump mounted on a portable computer, etc. by the technology of the present invention, a method of assembling a pump with a simple structure and a more stable performance, especially when miniaturization is essential Can provide.

The top view of the pump in the 1st and 2nd embodiment of the present invention A-A-A sectional view of FIG. The top view of the pump in the 1st and 3rd embodiment of the present invention B-O-B cross-sectional view of FIG. The top view of the member which covers the rotor of the pump in the 1st and 3rd embodiment of this invention The top view of the pump in the 1st, 2nd and 4th embodiment of the present invention CC sectional view of FIG. The top view of the pump in the 1st, 3rd and 5th embodiment of the present invention D-O-D sectional view of FIG. The top view of the pump in the 1st and 6th embodiment of the present invention Partial sectional view of FIG. Plan view showing an example of a conventional pump EO cross section of FIG.

Explanation of symbols

1 cylinder 21 rotor 22 rotor 23 rotor 24 rotor 25 rotor 3a vane 3b vane 3c vane 40a member covering rotor 40b member covering rotor 42a member covering rotor 42b member covering rotor 44a member covering rotor 44b member covering rotor 5 drive Shaft 6a Vane groove 6b Vane groove 6c Vane groove 7a Pump chamber 7b Pump chamber 7c Pump chamber 8 Shielding member 9 Shielding member 10a Partition 10b Partition 10c Partition

Claims (6)

A cylinder and a rotating rotor are provided in the cylinder, and a groove is provided in the rotating rotor, and a vane is disposed so as to be slidable as the rotor rotates. In the pump in which the member covering the rotor is disposed, the end of the rotor is forcibly rotated after assembling the member covering the rotor so as to contact the end of the rotor arranged opposite to the rotor in advance. An assembly method of a pump, wherein the shape of the sliding portions of the two members in contact with each other is assembled to each other by sliding the member on the member covering the rotor. The shape of the end of the rotor that is disposed opposite to the member that covers the rotor is made substantially convex, and after assembling the rotor end in advance with the member that covers the rotor, the rotor end is moved to the member that covers the rotor by forcibly rotating the rotor. 2. The method of assembling a pump according to claim 1, wherein the substantially convex shape part of the part is slid so that the shapes of the sliding parts of both members are adjusted to each other. About the member that covers the rotor, after forming an approximately convex raised portion with respect to the rotation center of the rotor at the portion where the rotor end portion is opposed, and assembling the rotor end portion in advance, 2. The assembly according to claim 1, wherein the rotor ends are slid into a substantially convex portion provided on a member that covers the rotor by forced rotation, and the shapes of the sliding portions of both members are made to conform to each other. A method for assembling the pump according to claim 1. A member that is relatively softer than the member that covers the rotor is disposed on a part of the rotor end portion that is disposed to face the member that covers the rotor, so that the member comes into contact with the member that covers the rotor in advance. 2. The assembly according to claim 1, wherein after the assembly, the rotor is forcibly rotated so that the soft member is slid on the member covering the rotor so that the shapes of the sliding portions of the two members become compatible with each other. Item 3. A method for assembling the pump according to Item 2. For the member that covers the rotor, a member that is relatively softer than the rotor is arranged in a portion that faces the rotor end so as to have a generally convex shape with respect to the rotation center of the rotor, and this is in contact with the end of the rotor in advance. 2. After assembling so that the rotor is forcibly rotated, the end of the rotor is slid on the soft member so that the shapes of the sliding portions of the two members become compatible with each other. A method for assembling the pump according to claim 3. A substantially annular partition wall is disposed at the end of the rotor facing the member covering the rotor so as to be substantially concentric with the rotation center of the rotor, so that the partition wall comes into contact with the member covering the rotor in advance. After the assembly, the rotor is forcibly rotated so that the substantially annular partition wall is slid on the member covering the rotor, and the shapes of the sliding portions of both members are adjusted to each other and assembled. Item 2. A method for assembling the pump according to Item 1.

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