JP7164447B2 - Rotating machine pipe mounting structure - Google Patents

Description

TECHNICAL FIELD The present invention relates to a pipe mounting structure for a rotating machine, and more particularly to a structure for mounting a pipe through which fluid flows between a fluid passage provided in a case and an elastic member in the case.

(a) A pipe arranged in a case of a rotating machine such as an electric motor or a generator, through which a lubricating and/or cooling fluid flows between a fluid passage provided in the case, and (b ) A cylindrical shape in which at least the outer peripheral surface of the pipe is attached to a cylindrical connecting end portion and pressed against the peripheral edge of the opening of the fluid passage opening on the inner surface of the case so that the pipe communicates with the fluid passage. There is known a pipe mounting structure for a rotating machine having an elastic member of The device described in Patent Document 1 is an example of this, and an elastic member is fitted to the outer peripheral side of the connection end of the pipe, and the outer peripheral surface of the elastic member has a tapered shape, and the inner surface of the case. It is concentrically positioned by being pressed against the tapered surface of the opening peripheral portion of the fluid passage provided in the .

JP 2012-23812 A

However, in such a conventional pipe mounting structure, when the elastic member is pressed against the tapered surface provided on the periphery of the opening of the fluid passage, if the amount of compressive deformation in the axial direction increases due to dimensional variations, etc., Since the load acts in a direction that reduces the diameter of the elastic member due to the action of the taper, the load may be applied to the outer peripheral surface of the connecting end of the pipe, causing damage (deformation, cracking, etc.) to the pipe.

The present invention has been made against the background of the above circumstances, and its object is to suppress damage to the pipe even when the amount of compressive deformation in the axial direction of the elastic member increases due to dimensional variations. It is to make

In order to achieve such an object, the first invention provides (a) a rotary machine which is disposed in a case of a rotating machine so that a lubricating and/or cooling fluid flows between it and a fluid passage provided in the case. (b) at least the outer peripheral surface of the pipe is attached to a cylindrical connection end portion, and is pressed against the opening peripheral edge portion of the fluid passage opening on the inner surface of the case to enter the fluid passage; and a cylindrical elastic member communicating with the pipes, wherein: (c) the peripheral edge of the opening of the fluid passage is flat, and the tip of the elastic member is perpendicular to the flat surface. (d) the elastic member includes a fitting portion fitted to the outer peripheral side of the connecting end portion of the pipe and the fitting portion protruding axially from the end face of the connecting end portion; (e) the inner diameter of the protrusion is smaller than the inner diameter of the fitting portion, and is formed at the boundary between the protrusion and the fitting portion; (f) the outer peripheral surface of the protruding portion has a diameter increasing from the boundary portion with the fitting portion toward the tip portion side; (g) the pipe is a resin pipe made of synthetic resin; (i) the fitting portion has an inner peripheral surface and an outer peripheral surface that are constant; and the thickness of the fitting portion is constant and thinner than the maximum thickness of the projecting portion at the boundary portion; It is attached to the connection end without using an adhesive by fitting the joint portion to the connection end, and in the assembled state, the fitting is performed by applying a pressing load to the elastic member. It is characterized in that the portion is flexurally deformed so as to bulge to the outer peripheral side .

A second invention is characterized in that, in the pipe mounting structure for a rotating machine according to the first invention, the pipe is a cooling pipe supplied with a cooling fluid that cools and lubricates each part of the rotating machine.

A third invention is the pipe mounting structure for a rotary machine according to the first invention or the second invention , wherein: (b) the tapered shape of the protruding portion is a tapered shape in which the outer diameter linearly decreases; The taper half angle is characterized by being in the range of 20° to 40°. In addition, the tapered shape in this specification is synonymous with the conical shape.

A fourth invention is the pipe mounting structure for a rotating machine according to any one of the first to third inventions, wherein: (a) the case is divided at an intermediate position in a direction parallel to the center line of the rotating machine; (b) the second case member is provided with the fluid passage, and the fluid passage opens on the inner surface of the second case member perpendicular to the center line; (c) the pipe has a straight shape and is attached to and held by the first case member in a posture parallel to the center line; (d) the connecting end of the pipe The second case member and the first case member move in a direction parallel to the center line in a state in which the elastic member attached to the portion is pressed against the peripheral edge of the opening of the fluid passage of the second case member. characterized in that they are butted against each other and integrally assembled with each other.

In such a pipe mounting structure for a rotating machine, the elastic member attached to the connection end of the pipe via the fitting portion includes a stepped portion that is brought into contact with the end surface of the connection end of the pipe, and the connection end. and a protruding portion protruding axially from the end face of the case, and the protruding portion presses perpendicularly against the flat opening peripheral edge of the fluid passage opening on the inner surface of the case, thereby causing the fluid to flow through the elastic member. A pipe communicates with the passage. In this case, since part of the pressing load when the elastic member is pressed against the opening peripheral portion is received by the end surface of the connecting end portion, the amount of compressive deformation of the elastic member in the axial direction due to dimensional variations is relatively large. Even if it becomes large, the pressing load can be properly received by the end face of the connection end. In addition, the protruding portion that is compressed in the axial direction by the pressing load has a tapered shape. Coupled with that, damage to the pipe is appropriately suppressed.

In addition, since the pipe is provided with an outward flange and the end of the fitting portion is brought into contact with the pipe, the pressing load is received by the outward flange in addition to the end face of the connecting end. , the fluid passage and the pipe can be reliably communicated with each other. The fitting portion that is brought into contact with the outward flange has cylindrical inner and outer peripheral surfaces each with a constant diameter, a thickness that is thinner than the maximum thickness of the protruding portion, and an expansion toward the outer peripheral side. By bending and deforming so as to protrude, an increase in pressing load accompanying compression is reduced, and application of an excessive load to the outward flange is suppressed.

In addition, resin pipes are used as pipes , but since resin pipes generally have lower strength than metal pipes and are easily damaged, the application of the present invention has the effect of suppressing damage to the pipes. obtained more appropriately. Since the resin pipe is lightweight and an insulator, it is possible to reduce the weight of the rotating machine and facilitate the processing of electrical parts.

A third aspect of the invention is a case in which a pipe is communicated with a fluid passage while sealing a gap between it and the peripheral edge of the opening of the fluid passage by an elastic member, and the protruding portion of the elastic member has a tapered shape in which the outer diameter linearly decreases, Since the taper half angle of the tapered shape is within the range of 20° to 40°, it is possible to reduce the increase in pressing load due to compression while ensuring the predetermined sealing performance, and to appropriately suppress damage to the pipe. That is, if the taper half angle is smaller than 20°, the effect of reducing the increase in pressing load due to compression is sufficient, although it varies depending on the material of the elastic member, the projecting dimension of the projecting portion, and the variation in the amount of compressive deformation in the axial direction. In addition, if the taper half angle exceeds 40°, the area of the tip of the protruding portion becomes small, impairing the sealing performance.

In the fourth aspect of the invention, the first case member and the second case member are separated at an intermediate position in the direction parallel to the center line of the rotating machine, and the first case member is arranged so that the straight pipe is parallel to the center line. The second case member and the second case member are connected to each other in a state in which the elastic member attached to and held by the case member and attached to the connection end of the pipe is pressed against the opening peripheral edge of the fluid passage of the second case member. 1 and the case member are abutted and integrally assembled. In this case, the amount of compressive deformation of the elastic member in the axial direction varies due to mounting errors of the pipe with respect to the first case member and dimensional errors of each part. properly obtained.

In addition, when an elastic member is attached to the connection end of the pipe attached to the first case member, and various parts are assembled in that state, the operator's hand or parts come into contact with the elastic member. there is a possibility. In that case, if the elastic member is only fitted to the connection end at the fitting portion, it may fall off the pipe. When an external force is applied from a lateral direction perpendicular to the pipe, a force component is generated in the direction of approaching the pipe, which prevents the pipe from falling off.

FIG. 1 is a diagram for explaining an example of a rotating machine having a pipe mounting structure of the present invention, and is a vertical cross-sectional view cut vertically along a first axis S1, which is the center line of the rotating machine. It is sectional drawing which expanded and showed the II part in FIG. 1, ie, the part in which the elastic member was arrange|positioned. FIG. 3 is a cross-sectional view showing the elastic member of FIG. 2 alone; FIG. 3 is a characteristic diagram showing the relationship between straight length L of an elastic member and sealing performance; The relationship between the axial pressing load F1 and the amount of compressive deformation C on the elastic member attached to the pipe is compared between this embodiment having a tapered projection and a comparative product having a cylindrical projection with a constant outer diameter. is a diagram showing the comparison. FIG. 6 is a diagram comparing shapes before compression deformation and in a state of compression deformation when the characteristics of FIG. 5 are measured for the present example. FIG. 10 is a characteristic diagram showing the result of examining the relationship between the external force F2 and the inclination angle of the projecting portion by applying an external force F2 from the lateral direction to the projecting portion of the present embodiment.

INDUSTRIAL APPLICABILITY The present invention is suitably applied, for example, to a pipe mounting structure for a rotating machine (electric motor or motor generator) used as a driving force source for a vehicle, but can also be applied to rotating machines other than vehicles. It is also possible to apply it to a rotating machine that is exclusively used as a generator. Cooling fluid cooled by an oil cooler is supplied to the pipe to cool , for example, the stator of the rotating machine or to lubricate each part of the rotating machine. It may be supplied without passing through an oil cooler. The fluid may be for cooling only, lubrication only, or both. For example, this pipe is configured in a straight line shape, but various modes are possible, such as bending, curving, or branching in the middle.

The outer peripheral surface of the connecting end of the pipe is, for example, a cylindrical shape with a constant outer diameter. Various modes are possible, such as a cylindrical shape and a cylindrical shape in which a plurality of annular grooves or annular projections are provided at predetermined intervals in the axial direction. The shape of the inner peripheral surface of the connection end portion can be determined appropriately, such as a cylindrical shape or a square tubular shape. The shape of the outer peripheral surface and the inner peripheral surface of the portion other than the connection end portion can also be determined appropriately, such as a cylindrical shape or a square tubular shape.

The pipe may only allow fluid to flow from the connecting end to the opposite end. That is, connection ends are provided at both ends in the longitudinal direction, and can be connected to fluid passages that open on both side surfaces of the case. In that case, the present invention may be applied to at least one of the mounting structures. Further, the end opposite to the connection end may be closed and a discharge hole or the like may be provided in the middle to allow the fluid to flow out. For example, a pipe is arranged substantially horizontally above the center line of the rotating machine on the outer peripheral side of the stator of the rotating machine which is arranged substantially horizontally, and the fluid flowing out from the discharge hole flows into the stator coil, the bearing, etc. supplied to cool or lubricate them. The arrangement posture of the pipe does not necessarily have to be horizontal or parallel to the center line of the rotating machine, and can be determined as appropriate. The arrangement posture of the rotating machine is also determined as appropriate.

The elastic member is made of an elastic material such as rubber, and when the projecting portion is pressed against the peripheral edge of the opening of the fluid passage, the elastic member is sealed so that the fluid does not leak from the peripheral edge of the opening, for example. The pipe is used to communicate with the fluid passage through the . Sealing performance is not necessarily required, and it is also possible to provide a groove or the like at the tip of the protruding portion to actively flow out part of the fluid. The tapered shape of the protruding portion of the elastic member is preferably a tapered shape in which the outer diameter linearly decreases, but the outer peripheral surface of the protruding portion has a recessed shape that is recessed toward the inner peripheral side or bulges toward the outer peripheral side compared to the tapered shape. A convex shape is also possible. The taper half angle of the tapered shape is suitable to be within the range of about 20° to 40°, but depending on the material of the elastic member (elastic modulus, etc.) and the projection dimension of the projection, the taper half angle may be set to less than 20° or 40°. It can also be larger than °. Also for tapered shapes other than tapered shapes, it is desirable that the average value of the gradient angle corresponding to the taper half angle is within a range of, for example, about 20° to 40°. The inner peripheral surface of the protruding portion is, for example, a cylindrical shape with a constant inner diameter. For example, it is also possible to provide a tapered shape in which the inner diameter increases linearly.

It suffices that the elastic member is pressed against both the outward flange and the end face of the connecting end portion in a state of being compressed and deformed at least in the axial direction. There may be gaps.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following examples, the drawings are appropriately simplified or modified for the sake of explanation, and the dimensional ratios, shapes, etc. of each part are not necessarily drawn accurately.

FIG. 1 is a diagram for explaining a rotating machine 10 having a pipe mounting structure according to one embodiment of the present invention, and is a vertical cross-sectional view taken along a first axis S1, which is the center line of the rotating machine 10. As shown in FIG. be. The rotating machine 10 is mounted on a vehicle in a position in which the first axis S1 is substantially horizontal and is used as a driving force source for running. It is a motor generator. The rotating machine 10 includes a cylindrical rotor 14 and a stator 16 which are arranged coaxially with the first axis S1 in a case 12. A cylindrical motor shaft 18 is fixed to the center of the rotor 14. there is

The case 12 includes a pair of first case member 20 and second case member 22 that are separated at an intermediate position in the direction parallel to the first axis S1. Both of the first case member 20 and the second case member 22 have bottomed cylindrical shapes, and are approached in a direction parallel to the first axis S1 so that their openings face each other. , are integrally assembled with each other by a plurality of bolts (not shown), and contain the rotor 14, the stator 16, and the like inside. A motor shaft 18 fixed to the rotor 14 is supported by the case 12 via a pair of bearings 24 and 26 so as to be rotatable about a first axis S1. It is coaxially fixed to the first case member 20 . The stator 16 can also be fixed to the first case member 20 by press fitting.

A cooling pipe 30 is arranged in the case 12 . The cooling pipe 30 is a pipe to which cooling fluid such as lubricating oil for cooling and lubricating each part of the rotating machine 10 is supplied. The cooling pipe 30 is an integrally molded synthetic resin pipe and has a straight shape, and is coaxially arranged on a second axis S2 that is parallel to the first axis S1 and defined above the first axis S1. It is That is, the cooling pipe 30 is arranged in the case 12 in a posture parallel to the first axis S<b>1 that is the centerline of the rotating machine 10 . The cooling pipe 30 has an elongated cylindrical shape, one end 32 of which is closed by a bottom and is positioned by being fitted in a mounting hole 34 provided in the first case member 20 . A mounting bracket 36 made of metal is integrally provided by insert molding at an intermediate position in the longitudinal direction of the cooling pipe 30 , and the mounting bracket 36 is fixed to the first case member 20 with bolts 38 . . The mounting bracket 36 and the mounting hole 34 integrally mount the cooling pipe 30 to the first case member 20 in a fixed posture coaxial with the second axis S2 parallel to the first axis S1. The cooling pipe 30 can also be configured by integrally joining a plurality of resin members such as halves divided along the longitudinal direction, for example.

The tip (other end) of the cooling pipe 30 attached to the first case member 20 by the attachment bracket 36 protrudes from the opening of the first case member 20 toward the second case member 22 and is attached to the elastic member. By being pressed by the pressing portion 42 of the second case member 22 via 40, it is positioned so as to be substantially coaxial with the second axis S2. The pressing portion 42 is provided at the bottom of the bottomed cylindrical second case member 22 . FIG. 2 is an enlarged cross-sectional view showing part II in FIG. A fluid passage 46 is opened in the pressing seat surface 44 of the pressing portion 42 . A cooling fluid such as lubricating oil cooled by an oil cooler 52 is supplied to the fluid passage 46 from an external pipe 50 connected to a connection port 48 shown in FIG. It is fed into the cooling pipe 30 from the fluid passage 46 . A plurality of discharge holes are provided at an intermediate position in the longitudinal direction of the cooling pipe 30, and the cooling fluid flowing out from the discharge holes is supplied to the coil of the stator 16, the bearings 24, 26, etc., and cools them. or lubricate. In addition to the fluid passage 46, the second case member 22 is provided with a fluid passage 54 and the like, and part of the cooling fluid supplied to the connection port 48 flows from the fluid passage 54 and the like to each part of the rotating machine 10. supplied. A mechanical oil pump that is rotationally driven by the motor shaft 18 or the like is integrally arranged in the case 12, and sucks fluid such as lubricating oil that has flowed back to the oil reservoir or the like in the case 12, and Alternatively, the fluid may be supplied to the fluid passages 46 and 54 without passing through the oil cooler 52 .

In FIG. 2, the cooling pipe 30 has a cylindrical connecting end 60 with a constant diameter on the outer and inner peripheral surfaces at the tip of the cooling pipe 30. The connecting end 60 has a cylindrical elastic member. 40 is installed. The elastic member 40 is pressed against the pressing seat surface 44 of the pressing portion 42 and is compressed and deformed, thereby positioning the connection end portion 60 of the cooling pipe 30 substantially coaxially with the second axis S2, thereby allowing the cooling pipe 30 to move toward the fluid. It communicates with the passage 46 and seals the gap between the elastic member 40 and the pressing bearing surface 44 so as to prevent the cooling fluid from leaking out. The fluid passage 46 is provided on the second axis S2, and the pressing seat surface 44 is a flat surface substantially perpendicular to the second axis S2, that is, to the first axis S1, which is the center line of the rotating machine 10. The distal end portion 72 of the elastic member 40 is pressed substantially perpendicularly to the pressing surface 44 . The pressing seat surface 44 constitutes the inner surface of the second case member 22 and corresponds to the peripheral edge of the opening of the fluid passage 46 .

FIG. 3 is a diagram showing the elastic member 40 alone, which is a cross-sectional view taken along the center line S3. As shown in FIG. It corresponds to a cross-sectional view cut along a second axis S2 substantially equal to the axis. The elastic member 40 is made of rubber, and has a fitting portion 62 fitted to the outer peripheral side of the connection end portion 60 of the cooling pipe 30 and a fitting portion 62 fitted so as to protrude from the end surface 60a of the connection end portion 60 in the axial direction. A protruding portion 64 is provided continuously and integrally with the joining portion 62 . The fitting portion 62 has a cylindrical inner peripheral surface and an outer peripheral surface with a constant diameter, and has a substantially uniform wall thickness. It is fitted to the outer peripheral surface of the connecting end portion 60 so as to be in close contact with the outer peripheral surface of the connection end portion 60 with dimensions that are substantially the same as or slightly smaller than the dimensions. The fitting portion 62 allows the elastic member 40 to be attached to the connecting end portion 60 of the cooling pipe 30 without using an adhesive. The axial length of the fitting portion 62 is substantially the same as the axial length of the connection end portion 60, and is an annular shape provided so as to be continuous in the axial direction of the connection end portion 60 and protrude toward the outer peripheral side. In the assembled state in which at least the elastic member 40 is axially compressed with respect to the outward flange 66 , the end portion of the fitting portion 62 on the side opposite to the projecting portion 64 abuts and is pressed against the outward flange 66 . It's like

The inner diameter of the protrusion 64 is smaller than the inner diameter of the fitting portion 62 , and a stepped portion 68 on the inner peripheral surface formed at the boundary between the protrusion 64 and the fitting portion 62 abuts the end face 60 a of the connecting end portion 60 . be touched. The inner diameter of the projecting portion 64 is smaller than the inner diameter of the connecting end portion 60, and in the assembled state in which the elastic member 40 is pressed against the pressing seat surface 44, the stepped portion 68 is pressed over the entire end surface 60a to receive the pressing load. be done. That is, as shown in FIG. 6B, the elastic member 40 according to the present embodiment is pressed against the pressing seat surface 44 and compressed and deformed in the axial direction in an assembled state in which the stepped portion 68 is aligned with the end surface 60a. In addition, the end of the fitting portion 62 is pressed against the outward flange 66, and the pressing load F1 is received by both of them. As shown in FIG. 6(a), in the natural state before being pressed against the pressing seat surface 44, between the stepped portion 68 and the end surface 60a and between the fitting portion 62 and the outward flange 66, Either one may have a gap. The elastic member 40 in FIG. 2 has a shape in a natural state before compression deformation, which is substantially the same as in FIGS. 3 and 6(a). The cooling pipe 30 is compressed and deformed in the axial direction by the pressing load F<b>1 , and communicates the cooling pipe 30 with the fluid passage 46 while sealing with the pressing seat surface 44 .

The outer peripheral surface 70 of the protruding portion 64 has a tapered shape in which the outer diameter linearly decreases from the boundary portion with the fitting portion 62 toward the tip portion 72 . , a tapered enlarged diameter portion 74 whose inner diameter linearly increases toward the distal end portion 72 is provided. Since the outer peripheral surface 70 has a tapered shape and the inner peripheral surface is provided with the enlarged diameter portion 74, the thickness of the protruding portion 64 becomes thinner toward the distal end portion 72, and the entire protruding portion 64 becomes thin. Since the volume of is reduced, an increase in the pressing load F1 when compressively deformed in the axial direction is reduced. The taper half angle θ of the tapered shape of the outer peripheral surface 70, ie, the inclination angle with respect to the center line S3, is determined within the range of 20° to 40°, and is about 30° in this embodiment. As the taper half angle θ increases, the volume decreases and the increase in the pressing load F1 is reduced. FIG. 4 shows the relationship between the straight length L and the sealing performance (the pressure at which the internal fluid leaks) by pressing the pressing seat surface 44 against the tip portion 72 of the projecting portion 64 with a constant pressing load F1 to supply the fluid to the inside. According to the characteristic diagram obtained by examining the relationship, it is necessary to secure a straight length of L1 or more that can obtain a predetermined required performance. Further, if the taper half angle θ becomes small, the effect of reducing the increase in the pressing load F1 due to volume reduction cannot be sufficiently obtained, so the taper half angle θ is preferably 20° or more.

FIG. 5 shows an example product and a cylindrical comparative product having a projection 64 with a constant outer diameter (taper half angle θ=0°). It is the result of adding F1 and investigating the relationship between the pressing load F1 and the amount C of compression deformation. As is clear from these results, the product of the present embodiment reduces the increase in the pressing load F1 compared to the comparative product, and the compression deformation amount C, which is determined in consideration of the dimensional error and assembly error of each part, is, for example, 1.5 mm. In the use range of about 3.0 mm, the load value is sufficiently lower than the upper limit F1max at which the cooling pipe 30 may be damaged. On the other hand, in the comparative product, the pressing load F1 exceeds the upper limit F1max before the compressive deformation amount C reaches 3.0 mm, and the cooling pipe 30 may be damaged. The decrease in the pressing load F1 of the comparative product when the amount of compressive deformation C is 3.0 mm or more is due to the damage to the cooling pipe 30 .

The step portion 68 of the elastic member 40 is pressed against the end surface 60 a and the end portion of the fitting portion 62 is pressed against the outward flange 66 . The fitting portion 62 to be brought into contact has cylindrical inner and outer peripheral surfaces each having a constant diameter, and has a constant thickness, which is thinner than the maximum thickness of the protruding portion 64 having a small inner diameter. The maximum thickness of the protruding portion 64 is the thickness of the portion having the largest outer diameter at the boundary portion with the fitting portion 62 . Also, the thickness of the fitting portion 62 is smaller than the axial length of the fitting portion 62 . As a result, as indicated by arrow A in FIG. 6(b), the fitting portion 62 is flexurally deformed so as to bulge out toward the outer periphery, thereby reducing the increase in the pressing load F1 due to the compression. Application of an excessive load to the flange 66 is suppressed. In other words, the radial dimension r (see FIG. 3) of the outer peripheral surface of the fitting portion 62 is a thickness that causes the fitting portion 62 to flex and deform so as to bulge outward when the pressing load F1 is applied. is defined as

As described above, in the pipe mounting structure of the rotating machine 10 of the present embodiment, the elastic member 40 attached to the connection end portion 60 of the cooling pipe 30 via the fitting portion 62 is attached to the end face 60a of the connection end portion 60. It has a stepped portion 68 to be brought into contact with and a projecting portion 64 projecting axially from the end surface 60 a of the connecting end portion 60 . , the cooling pipe 30 is communicated with the fluid passage 46 provided in the second case member 22 while sealing with the pressing seat surface 44 . In this case, since part of the pressing load F1 when the elastic member 40 is pressed against the pressing seat surface 44 is received by the end surface 60a of the connecting end portion 60, the axial direction of the elastic member 40 may vary due to dimensional variations and the like. Even when the amount of compressive deformation C becomes relatively large, the pressing load F1 is appropriately received by the end surface 60a. In addition, the projecting portion 64 that is axially compressed by the pressing load F1 has a tapered shape, and the volume is reduced by the tapered portion to reduce the increase in the pressing load F1 due to the compression. Coupled with the fact that the load F1 is received by the end face 60a, damage to the cooling pipe 30 is appropriately suppressed.

In addition, the cooling pipe 30 is provided with an outward flange 66, and the end of the fitting portion 62 is brought into contact with the outward flange 66. The pressure load F1 can be received by the pressure load F1 as well, and the fluid passage 46 and the cooling pipe 30 can be reliably communicated with each other while appropriately ensuring a predetermined sealing performance by the pressure load F1. The fitting portion 62 that is brought into contact with the outward flange 66 has cylindrical inner and outer peripheral surfaces each having a constant diameter and a thickness that is thinner than the maximum thickness of the protruding portion 64. As shown in FIG. 6(b), the outward flange 66 is flexurally deformed so as to bulge out to the outer peripheral side, and the increase in the pressing load F1 due to compression is reduced, and an excessive load is applied to the outward flange 66. Suppressed.

In addition, a resin pipe is used as the cooling pipe 30, and since the resin pipe has lower strength than a metal pipe and is easily damaged, the elastic member 40 having the fitting portion 62 and the projecting portion 64 is used. Therefore, the effect of suppressing damage to the cooling pipe 30 can be obtained more appropriately. Since the resin pipe is lightweight and an insulator, the weight of the rotating machine 10 can be reduced, and the processing of electrical parts such as electrical wiring can be facilitated.

The cooling pipe 30 is communicated with the fluid passage 46 while the elastic member 40 seals the pressure bearing surface 44, and the outer diameter of the outer peripheral surface of the projecting portion 64 of the elastic member 40 linearly decreases. Since it has a tapered shape and the taper half angle θ of the tapered shape is within the range of 20° to 40°, the cooling pipe 30 is prevented from being damaged by reducing an increase in the pressing load F1 due to compression while ensuring a predetermined sealing performance. can be suppressed appropriately.

Further, the case 12 includes a first case member 20 and a second case member 22 which are divided at an intermediate position in a direction parallel to the first axis S1, which is the center line of the rotating machine 10, and which are straight cooling pipes. 30 is attached to and held by the first case member 20 in a posture parallel to the first axis S1, and the elastic member 40 attached to the connecting end portion 60 of the cooling pipe 30 is attached to the second case member 22. The first case member 20 and the second case member 22 are butted against each other and integrally assembled with bolts (not shown) while being pressed against the pressing seat surface 44 which is the peripheral edge of the opening of the fluid passage 46 . In this case, the amount of compressive deformation C of the elastic member 40 in the axial direction varies due to mounting errors of the cooling pipe 30 with respect to the first case member 20 and dimensional errors of each part. The effect of suppressing damage to the cooling pipe 30 can be appropriately obtained by using 40 .

In addition, when the elastic member 40 is attached to the connection end portion 60 of the cooling pipe 30 attached to the first case member 20, and various parts are assembled in this state, the operator's hands and the parts may be damaged. There is a possibility of contact with the elastic member 40 . In that case, since the fitting portion 62 of the elastic member 40 is only fitted to the connection end portion 60 in this embodiment, there is a possibility that the elastic member 40 may come off from the connection end portion 60 . For example, before assembling the second case member 22 to the first case member 20 in FIG. When the stator 18, the rotor 14, etc. are assembled in the first case member 20, the cooling pipe 30 protrudes upward from the opening of the first case member 20, so that the elastic member 40 may be brought into contact with the connecting end portion. If it falls out of 60, it falls to the bottom of the first case member 20 and is difficult to remove.

On the other hand, since the projecting portion 64 of the elastic member 40 of this embodiment has a tapered shape, an external force F2 was applied from a lateral direction perpendicular to the center line S3 as shown in FIG. In this case, a component of force is generated in the direction (downward in FIG. 3) approaching the connection end 60, thereby suppressing the falling off. FIG. 7 shows an external force F2 applied laterally to the projecting portion 64 of the elastic member 40 attached to the connection end portion 60, and the external force F2 and the inclination angle of the center line S3 of the projecting portion 64, that is, the angle of inclination of the cooling pipe 30. A characteristic diagram showing the results of examining the relationship between the bending angle with respect to the second axis S2, which is the center line, and is a graph of the portion where the inclination angle exceeds 45°. , there is a high possibility that the fitting portion 62 will come out of the connecting end portion 60 and the elastic member 40 will drop out of the cooling pipe 30 . That is, if the external force F2 is lower than the upper limit value F2max, the attachment state of the elastic member 40 to the connection end portion 60 is properly maintained. In FIG. 7, the reduction in the external force F2 at the portion where the protrusion 64 has a large inclination angle is due to the elastic member 40 slipping out of the connection end 60. As shown in FIG.

As described above, the embodiments of the present invention have been described in detail with reference to the drawings. However, this is only one embodiment, and the present invention can be implemented in a mode in which various modifications and improvements are added based on the knowledge of those skilled in the art. can be done.

10: Rotating Machine 12: Case 20: First Case Member 22: Second Case Member 30: Cooling Pipe (Pipe, Resin Pipe) 40: Elastic Member 44: Pressing Seat (Inner Side, Opening Periphery) 46: Fluid Passage 60: Connection end portion 60a: End surface 62: Fitting portion 64: Protruding portion 66: Outward flange 68: Stepped portion 70: Outer peripheral surface 72: Tip portion S1: First axis (center line of rotating machine) F1: Pressing load θ: taper half angle

Claims (4)

a pipe disposed in a case of the rotating machine, through which a lubricating and/or cooling fluid flows between a fluid passage provided in the case;
At least the outer peripheral surface of the pipe is attached to a cylindrical connecting end portion, and is pressed against the peripheral edge of the opening of the fluid passage opening on the inner surface of the case to connect the pipe to the fluid passage. an elastic member;
In a pipe mounting structure for a rotating machine having
The peripheral edge of the opening of the fluid passage is a flat surface, and the tip of the elastic member is pressed perpendicularly to the flat surface,
The elastic member includes a fitting portion fitted to the outer peripheral side of the connecting end portion of the pipe, and a fitting portion continuously integrally provided so as to protrude from the end surface of the connecting end portion in the axial direction. and a protrusion,
The inner diameter of the projection is smaller than the inner diameter of the fitting portion, and the stepped portion of the inner peripheral surface formed at the boundary between the projection and the fitting portion is brought into contact with the end surface of the connection end. ,
The outer peripheral surface of the protruding portion has a tapered shape in which the diameter dimension decreases from the boundary portion with the fitting portion toward the tip portion side ,
The pipe is a resin pipe made of synthetic resin,
The pipe is provided with an outward flange with which an end portion of the fitting portion opposite to the projecting portion abuts at least in an assembled state in which the elastic member is pressed against the opening peripheral portion. ,
The fitting portion has a cylindrical shape with an inner peripheral surface and an outer peripheral surface each having a constant diameter dimension, and the thickness of the fitting portion is constant and is larger than the maximum thickness of the protrusion at the boundary portion. is also thin ,
The elastic member is attached to the connecting end portion without using an adhesive by fitting the fitting portion to the connecting end portion, and in the assembled state, a pressing load is applied to the elastic member. By being applied, the fitting portion is flexurally deformed so as to bulge to the outer peripheral side.
A pipe mounting structure for a rotating machine, characterized by: The pipe mounting structure for a rotating machine according to claim 1 , wherein the pipe is a cooling pipe supplied with a cooling fluid that cools and lubricates each part of the rotating machine. The elastic member communicates the pipe with the fluid passage while sealing a gap with the opening rim of the fluid passage when the tip of the projecting portion is pressed against the rim of the opening of the fluid passage.
3. The tapered shape according to claim 1 or 2 , wherein the tapered shape of the projecting portion is a tapered shape in which the outer diameter linearly decreases, and the taper half angle of the tapered shape is within the range of 20° to 40°. Rotating machine pipe mounting structure. The case includes a first case member and a second case member divided at an intermediate position in a direction parallel to the center line of the rotating machine,
The second case member is provided with the fluid passage, and the fluid passage is opened on an inner surface of the second case member perpendicular to the center line,
The pipe has a straight shape and is attached to and held by the first case member in a posture parallel to the center line,
The second case member and the first case member are connected to each other in a state in which the elastic member attached to the connection end portion of the pipe is pressed against the opening peripheral edge portion of the fluid passage of the second case member. The pipe mounting structure for a rotary machine according to any one of claims 1 to 3 , characterized in that the pipe mounting structures are integrally assembled with each other by butting each other in a direction parallel to the center line.

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