JP2023015883A - Housing for motor - Google Patents

Abstract

To improve strength to suppress deformation when a refrigerant piping is press fit into a communication port of a refrigerant passage.SOLUTION: A housing for a motor is constituted of: an annular inner cylinder which can accommodate a stator and a rotor of the motor inside; and an outer cylinder which accommodates the inner cylinder inside. A refrigerant passage is formed between the inner cylinder and the outer cylinder. The outer cylinder comprises: a communication port which is formed on an outer peripheral side surface of the outer cylinder and causes the refrigerant piping outside the housing and the refrigerant passage to communicate with each other; and a projection which is formed to project in an outer peripheral direction at a position different from a formation position of the communication port on the outer peripheral side surface. The projection is formed to project along a center line of the communication port. The center line passes through a position deviated from a rotational center of the motor which is accommodated inside the inner cylinder.SELECTED DRAWING: Figure 4

Description

The present invention relates to a motor housing.

In recent years, the amount of heat generated during operation has increased with the increase in the output of motors mounted on vehicles and the like. In view of this, a cooling structure has been studied in which a flow path is formed inside a housing that accommodates the motor by removing light or the like, and a coolant flows through the flow path to cool the entire motor (Patent Document 1).

JP 2010-041835 A

Among motors mounted on vehicles, there are motors whose housings are constructed of double pipes for miniaturization. A housing having a double-tube structure is composed of an outer cylinder and an inner cylinder, and a coolant channel is defined between the outer cylinder and the inner cylinder. In a motor using such a housing with a double-tube structure, attempts have been made to reduce the thickness of constituent members of the housing in order to reduce the weight and improve the cooling efficiency. Therefore, when stress acts on the outer cylinder, for example, when a refrigerant pipe is press-fitted into a refrigerant inlet formed in the outer cylinder and fixed, the outer cylinder itself deforms due to the load applied at the time of press-fitting. There is a risk.

A motor housing according to one aspect of the present invention includes an inner cylinder capable of accommodating a stator and a rotor of a motor therein, and an outer cylinder accommodating the inner cylinder. A flow path is formed. The outer cylinder is formed on the outer peripheral side surface of the outer cylinder, and protrudes in the outer peripheral direction at a position different from the formation position of the communication port that communicates the refrigerant pipe and the refrigerant flow path outside the housing and the communication port on the outer peripheral side surface. and a protrusion formed to: The protrusion is formed to protrude along the center line of the communication port. The centerline passes through a position off the center of rotation of the motor housed inside the inner cylinder.

According to the motor housing of the present invention, it is possible to improve the strength and suppress deformation when the refrigerant pipe is press-fitted into the communication port of the refrigerant flow path.

1 is a perspective view showing a housing according to an embodiment; FIG. FIG. 2 is an exploded perspective view of the housing. FIG. 3 is a perspective view of the housing from the other direction. FIG. 4 is a cross-sectional view in the IV section of FIG. FIG. 5 is a cross-sectional view of a housing in another example of protrusion structure.

Embodiments of the present invention will be described below with reference to the drawings.

1 is a perspective view of a housing according to an embodiment of the present invention; FIG. 2 is an exploded perspective view of the housing shown in FIG. 1; FIG. In FIGS. 1 and 2, the opening of the housing that accommodates the motor (not shown) is shown facing right.

As shown in FIGS. 1 and 2, the housing 1 includes an outer cylinder 2 having a cylindrical opening 2A and a cylindrical inner cylinder 3 provided within the opening 2A. The inner cylinder 3 has a cylindrical opening 3A, and a stator is attached to the opening 3A. A rotor is arranged inside the stator, and the rotor, stator, and housing 1 constitute a motor.

As shown in FIG. 1, the outer cylinder 2 has an accommodating portion 4 in which an inverter (not shown) is accommodated. The inverter converts DC power supplied from a battery (not shown) into AC power. The converted AC power is supplied to the coils of the motor, thereby driving the motor to rotate. A coolant channel is formed between the inner peripheral surface of the outer cylinder 2 and the outer peripheral surface of the inner cylinder 3 .

The outer cylinder 2 has an inflow port 5 and an outflow port 6 for the refrigerant on the outer peripheral side surface on the left side of the figure. The inflow port 5 and the outflow port 6 are configured so as to have a linear coolant flow path therein. The inlet 5 and the outlet 6 are aligned along the center of rotation of the motor (the center of the rotor shaft) and are arranged at the same position (height) in the circumferential direction. Press-fit connectors 7 and 8 are attached to the inlet 5 and the outlet 6, respectively. The press-fit connectors 7 and 8 have one inner end press-fitted into the inlet 5 and the outlet 6 and the other outer end connected to a refrigerant pipe (not shown) outside the housing 1 .

Refrigerant taken in from the outside of the housing 1 through the press-fit connector 7 and the inlet 5 flows through the refrigerant flow path formed between the outer cylinder 2 and the inner cylinder 3, and cools the entire motor through heat exchange. , outflow port 6 and press-fit connector 8 to the outside of housing 1 .

As shown in FIG. 2, the inner cylinder 3 includes a cylindrical portion 10 and flange-like end portions 11A and 11B protruding radially outward at both ends of the cylindrical portion 10 in the axial direction. The outer diameter of one end portion 11A accommodated inside the opening portion 2A is substantially the same as the inner diameter of the opening portion 2A of the outer cylinder 2, and the outer diameter of the other end portion 11B is the same as the inner diameter of the opening portion 2A of the outer cylinder 2. It is larger than the inner diameter of the portion 2A. Therefore, when the inner cylinder 3 is inserted into the outer cylinder 2 , the end portion 11</b>B protrudes from the outer peripheral side surface of the outer cylinder 2 and is locked. With this configuration, when the inner cylinder 3 is inserted into the opening 2A of the outer cylinder 2, the space between the outer peripheral surface of the inner cylinder 3 and the inner peripheral surface of the cylindrical portion 10 of the outer cylinder 2 is Both ends are sealed by the end portions 11A and 11B to form a coolant channel.

FIG. 3 is a perspective view of the housing 1 viewed from another direction. In this figure, the opening 2A of the outer cylinder 2 is shown facing leftward in the figure.

Two bosses 12 and 13 are provided on the outer peripheral side surface of the outer cylinder 2 on an extension line (hereinafter referred to as the center line X) of the center line of each flow path of the inlet 5 and the outlet 6. there is The boss 12 is arranged in the same plane as the inlet 5, and the boss 13 is arranged in the same plane as the outlet 6, in the plane in the radial direction (cross-sectional direction of the motor) perpendicular to the rotation center Y of the motor. be done. Furthermore, the bosses 12 and 13 are aligned in the direction along the rotation center Y of the motor on the outer peripheral side surface of the outer cylinder 2 .

Furthermore, various ribs are provided on the outer peripheral side surface of the outer cylinder 2 in order to increase the strength of the outer cylinder 2 . Specifically, a first reinforcing rib 9 having a long circumferential length and a second reinforcing rib 14 having a short circumferential length are radially provided along the outer peripheral side surfaces with the bosses 12 and 13 as starting points. The first reinforcing rib 9 extends in an arc shape from the lower portions of the bosses 12 and 13 along the outer peripheral side surface of the outer cylinder 2 to the inlet 5 and the outlet 6 (see FIG. 1). The second reinforcing ribs 14 are formed in pairs with respect to the bosses 12 and 13 and extend radially from the bosses 12 and 13 .

In this way, the bosses 12 and 13 are structural bodies having the first reinforcing rib 9 and the pair of second reinforcing ribs 14 on the side surfaces, and a certain level of strength is ensured. Further, the bosses 12 and 13 have flat end surfaces 12A and 13A in the projecting direction. In addition, since the inlet 5 and the outlet 6 are provided with the first reinforcing ribs 9 on the side surfaces, their strength is enhanced.

4 is a cross-sectional view of the outer cylinder 2 of the housing 1. FIG. This figure shows a cross section of the outer cylinder 2 in the direction perpendicular to the rotation center Y of the motor (cross-sectional direction of the motor) in section IV of FIG.

As shown in this drawing, the inlet 5 and the boss 12 are located on opposite sides of the housing portion 4 in the upper portion of the outer cylinder 2 in the horizontal direction of the drawing, that is, at positions facing each other across the rotation center Y of the rotor. is provided. Further, the inlet 5 and the boss 12 are provided above the rotation center Y of the motor inserted into the housing 1 (the center axis Y of the opening 2A of the outer cylinder 2) in the vertical direction of the figure. In addition, in the present embodiment, the inlet 5 is provided closer to the accommodating portion 4 than the boss 12 is.

More specifically, the boss 12 is formed to rise from the outer peripheral side surface of the outer cylinder 2 along the extension of the center line X of the inlet 5 . On the inner peripheral surface of the outer cylinder 2, the points of intersection with the center line X of the flow path direction of the inlet 5 are an intersection point 5X with the flow path center of the inlet 5 and an intersection point 12X with the central axis of the boss 12. be provided. Then, the angle formed by the line connecting the intersection 5X of the flow path center of the inlet 5 and the rotation center Y and the line connecting the intersection 12X of the central axis of the boss 12 and the rotation center Y is a predetermined angle Z. is provided in The predetermined angle Z is, for example, 90 to 120 degrees, preferably 120 degrees, and is an angle obtained experimentally for optimally press-fitting the press-fit connector 7 into the inlet 5, which will be described later.

This figure shows the first reinforcing rib 9 and the second reinforcing rib 14 provided along the outer peripheral side surface of the outer cylinder 2 from the side surface of the boss 12 . A tip surface 12A of the boss 12 is configured as a plane perpendicular to the center line X in the direction of the flow path. In this figure, the boss 12 has a hollow portion and is recessed, but the boss 12 may not have a hollow portion.

One end of a press-fit connector 7 is press-fitted and fixed inside the tip of the inlet 5 in the outer cylinder 2 . A refrigerant pipe (not shown) is connected to the other end of the press-fit connector 7 so as to introduce refrigerant from the outside of the housing 1 into the refrigerant flow path inside the housing 1 .

When press-fitting the press-fit connector 7 into the inlet 5, first, the front end surface 12A of the boss 12 is brought into contact with a fixing jig (not shown) and fixed. Thereby, the boss 12 functions as a load receiving portion in a state of being locked to the fixing jig. Then, one end of the press-fit connector 7 is applied to the tip of the inlet 5, and a load is applied to the press-fit connector 7 in a direction toward the inlet 5 along the direction of the flow path (center line X), thereby closing the press-fit connector 7. It is inserted into the inflow port 5 and press-fitted and fixed.

If the inflow port 5 and the boss 12 are not provided on the same extension line of the center line X, when the press-fit connector 7 is press-fitted into the inflow port 5, a rotational force around the boss 12 will act. It is difficult to apply a load along the centerline X. However, in this embodiment, since the boss 12 is provided on the extension line of the center line X of the inlet 5, no rotational force is generated around the boss 12, so that the load is applied along the center line X. The press-fitting connector 7 can be smoothly press-fitted into the inlet 5 when applying voltage.

Two intersection points of the extension of the center line X and the inner peripheral surface of the outer cylinder 2, that is, the intersection point 5X with the center line X of the inlet 5 and the intersection point 12X with the central axis of the boss 12 are the rotation center Y is arranged to form an angle of 120 degrees with respect to Here, when the outer cylinder 2 is thinned, the outer cylinder 2 is likely to be deformed when stress acts on the outer peripheral side surface of the outer cylinder 2 in the radial direction toward the rotation center Y of the motor. However, in the present embodiment, since the pressing load F applied during press-fitting is shifted from the direction toward the rotation center Y, the radial load f1 in the direction toward the rotation center Y and the radial load f1 and an orthogonal surface direction load f2.

By dividing the pressing load F into the radial direction and the other directions in this way, part of the force (f2) is relieved at the intersection 5X in the tangential direction with respect to the outer peripheral side surface of the outer cylinder 2, and the radial direction load f1 is released. Since it can be made smaller than the pressing load F, deformation of the outer cylinder 2 in the radial direction can be suppressed. A load f2 in the surface direction is generated along the outer peripheral surface of the outer cylinder 2, but since the strength of the arc portion forming the outer periphery of the outer cylinder 2 is relatively high, deformation of the outer cylinder 2 in the surface direction is unlikely to occur. In this manner, deformation of the outer cylinder 2 can be suppressed as a whole.

Here, the inlet 5 (5X) and the boss 12 (12X) are arranged so as to form an angle of 120 degrees with respect to the rotation center Y. When the predetermined angle Z is larger than 120 degrees, the angle formed by the pressing load F and the radial load f1 becomes smaller. Although the radial load f1 becomes a large value closer to the pressing load F, the predetermined angle Z becomes 180 degrees and the inlet 5 (5X) and the boss 12 (12X) are arranged so as to face each other. becomes equal to the pressing load F, the deformation of the outer cylinder 2 can be suppressed.

The predetermined angle Z may be less than 120 degrees, and more specifically, the predetermined angle Z may be 90 degrees or less. When the predetermined angle Z is less than 90 degrees, the angle between the pressing load F and the radial load f1 is greater than 45 degrees. Therefore, if the pressing load F is decomposed into the radial load f1 and the surface direction load f2, the radial load f1 becomes smaller than the surface direction load f2. As a result, most of the stress acts in the surface direction, and radial deformation of the outer cylinder 2 can be suppressed more reliably.

When a motor including the housing 1 is mounted on a vehicle, the bosses 12 and 13 may be sound and vibration measurement bosses to which a sensor for detecting sound and vibration of the motor is attached when checking the sound and vibration before shipment, or motors. A harness fixing boss used to fix a harness for electrically connecting various devices when installed in a room. Further, when the motor is integrated with the gearbox, an oil passage is provided inside the outer cylinder 2 for supplying the oil of the gearbox. Bosses 12, 13 may be utilized.

Further, the load receiving portion when the press-fit connector 7 is inserted into the inlet 5 and press-fitted is not limited to the bosses 12 and 13 . As shown in FIG. 5, it may be a projecting structure 15 which is a solid structure projecting from the outer peripheral side surface of the outer cylinder 2 and has a flat tip surface 12A in the projecting direction and a stamped area. . The stamping area is stamped with an authentication number of a government agency, a service number, or the like. Such a projecting structure 15 can be used as a load receiving portion in a state of being locked by a fixing jig when the press-fit connector 7 is inserted into the inflow port 5 and press-fitted and fixed, not limited to stamping. can.

According to the motor housing 1 of this embodiment, the following effects can be obtained.

According to the housing 1 of the present embodiment, the outer cylinder 2 has an inlet 5 and an outlet 6 (communication port) which are formed on the outer peripheral side surface of the housing 1 and communicate with the refrigerant pipes outside the housing 1 and the refrigerant flow path configured inside. ), and bosses 12 and 13 (protrusions) formed to protrude in the outer peripheral direction at positions different from the formation positions of the inlet 5 and the outlet 6 on the outer peripheral side surface. Bosses 12 and 13 are formed to protrude along the center line X of inlet 5 and outlet 6 . A centerline X of the inlet 5 and the outlet 6 passes through a position deviated from the rotation center Y of the rotor housed inside the inner cylinder 3 .

Press-fit connectors 7 and 8 connected to refrigerant pipes are press-fitted to the inlet 5 and the outlet 6 and fixed. Such press-fitting is performed by applying a pressing load F to the press-fit connectors 7 and 8 against the inlet 5 and the outlet 6 while applying the tip surfaces 12A and 13A of the bosses 12 and 13 with a fixing jig. When the pressing load F is applied in this manner, stress acts on the outer surface of the outer cylinder 2 .

Here, since the outer cylinder 2 is a tubular member, it is easily deformed in the radial direction when stress acts toward the rotation center Y on the outer peripheral side surface. However, in this embodiment, the center line X of the inlet 5, which is the direction in which the pressing load F is applied, is offset from the direction from the inlet 5 toward the rotation center Y. As shown in FIG.

Therefore, the pressing load F generated in the direction of the center line X can be decomposed into a radial load f1 and a surface direction load f2. Since the radial load f1 is smaller than the pressing load F, radial deformation of the outer cylinder 2 is suppressed. At the same time, the load f2 in the surface direction is generated along the outer circumference of the outer cylinder 2, but since the strength of the arc portion of the outer circumference of the outer cylinder 2 is relatively high, the deformation of the outer cylinder 2 in the surface direction is unlikely to occur. In this manner, deformation of the outer cylinder 2 can be suppressed as a whole.

According to the housing 1 of this embodiment, the bosses 12 and 13 are provided with the first reinforcing ribs 9 and the second reinforcing ribs 14 that connect the side surfaces of the bosses 12 and 13 to the outer peripheral side surface of the outer cylinder 2 . With such a configuration, the strength of the bosses 12 and 13 is improved in addition to the strength of the outer cylinder 2, so that the press-fit connectors 7 and 8 can be reliably used as load receivers when the press-fit connectors 7 and 8 are press-fitted into the inlet 5 and the outlet 6. will function as

According to the housing 1 of this embodiment, the bosses 12 and 13 are sound and vibration measurement bosses or harness fixing bosses. By sharing the bosses 12 and 13 that receive the load during press-fitting and fixing with bosses for other purposes such as sound and vibration measurement bosses or harness fixing bosses, the overall configuration can be simplified. In particular, since the motor vibrates during operation, it must be spaced apart in order to secure a clearance when arranging it in the motor room, which is a significant space constraint. In this way, by using the configuration of the bosses 12 and 13 for other than the load receiving portion other than when press-fitting, it is possible to improve the layout in the motor room.

According to the housing 1 of the present embodiment, the projecting structure 15 is solid so as to project from the outer peripheral side surface of the outer cylinder 2, and the tip end surface 12A in the projecting direction is flat and has a stamped area. may be provided. Such a projecting structure 15 can be used as a load receiving portion in a state of being locked by a fixing jig when the press-fit connector 7 is inserted into the inflow port 5 and press-fitted and fixed, not limited to stamping. can. In this way, by using the configuration of the projecting structure 12 for other than the load receiving portion other than when press-fitting, it is possible to improve the layout in the motor room.

According to the housing 1 of this embodiment, the inlet 5 and the boss 12 are arranged to form a predetermined angle Z with respect to the rotation center Y of the motor, and the predetermined angle Z is 90 to 120 degrees. is. In such a configuration, as shown in FIG. 4, the angle between the pressing load F and the radial load f1 is 45 degrees or less. As a result, the distance between the inflow port 5 and the boss 12 becomes longer, which makes it easier to press-fit the press-fit connector 7 into the inflow port 5 while suppressing deformation of the outer cylinder 2 .

Although the embodiments of the present invention have been described above, the above embodiments merely show a part of application examples of the present invention, and the technical scope of the present invention is not limited to the specific configurations of the above embodiments. do not have.

Reference Signs List 1 housing 2 outer cylinder 2A opening 3 inner cylinder 5 inlet 6 outlet 7, 8 press-fit connector 12, 13 boss

Claims (6)

It is composed of an annular inner cylinder capable of accommodating the stator and rotor of the motor inside, and an outer cylinder accommodating the inner cylinder inside, and a coolant flow path is formed between the inner cylinder and the outer cylinder. A housing for a motor,
The outer cylinder is
a communication port formed in the outer peripheral side surface of the outer cylinder and communicating between the refrigerant pipe outside the housing and the refrigerant flow path;
a protruding portion formed to protrude in the outer peripheral direction at a position different from the formation position of the communication port on the outer peripheral side surface,
The protrusion is formed to protrude along the center line of the communication port,
The motor housing, wherein the center line passes through a position away from the center of rotation of the motor housed inside the inner cylinder. The motor housing according to claim 1,
A housing for a motor, wherein a connecting portion for exchanging refrigerant with the outside of the housing is press-fitted and fixed in the communicating port along the center line of the communicating port. The motor housing according to claim 1 or 2,
The motor housing, wherein the protruding portion includes a rib extending from the side surface thereof along the outer peripheral side surface. A motor housing according to any one of claims 1 to 3,
The motor is mounted in a motor room of the vehicle,
The motor housing, wherein the projecting portion is a sound and vibration measurement boss or a harness fixing boss. A motor housing according to any one of claims 1 to 3,
The motor is mounted in a motor room of the vehicle,
The motor housing, wherein the projecting portion is a projecting structure having an engraving area on an end face in a projecting direction. A motor housing according to any one of claims 1 to 5,
A housing for a motor, wherein the communicating port and the projecting portion are arranged in the outer cylinder at positions forming an angle of 90 to 120 degrees with respect to the center of rotation of the motor.

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