JP6729969B2 - Pump device manufacturing method - Google Patents

Description

The present invention relates to a method for manufacturing a pump device used as a hydraulic pressure supply source for pressure fluid utilizing equipment.

Conventionally, in order to prevent muddy water from entering the inside of the pump device, the outer periphery of the cylindrical portion of the housing is press-fitted and fixed to a press-fitted portion of the cover member with a seal that extends in the pump drive axis direction. It was (For example, patent document 1).

JP-A-2014-177884

However, in the conventional pump device, internal stress is generated in the bent portion of the cover member by press-fitting the tubular portion of the housing into the press-fitted portion of the cover member. Further, since the inner peripheral surface of the press-fitted portion of the cover member including the bent portion is required to have high dimensional accuracy for press fitting, it is formed by machining, so that the metal material fiber flow is inside the bent portion. Since it is cut, it is disadvantageous in strength.
The present invention has been made in view of the above problems, and it is an object of the present invention to provide a method for manufacturing a pump device in which stress concentration in a bent portion of a cover member is relaxed.

In order to achieve the above object, in the pump device of the present invention, the inner peripheral surface of the press-fitted portion of the cover member is formed in a reverse taper shape whose radial dimension becomes smaller as the distance from the bent portion side increases.

The closer the press-fitted portion of the cover member is to the bent portion, the smaller the interference with the boss portion of the housing is, and the stress concentration at the bent portion can be relaxed.

3 is an axial sectional view of the variable displacement vane pump of Embodiment 1. FIG. 5 is a radial cross-sectional view of the variable displacement vane pump of Embodiment 1. FIG. FIG. 5 is a single-part view of the cover member according to the first embodiment. 5 is an enlarged view of the vicinity of a cover member of Example 1. FIG. FIG. 3 is an enlarged view of a main part near a cover member according to the first exemplary embodiment.

Hereinafter, a mode for realizing a method for manufacturing a pump device according to the present invention will be described based on an embodiment shown in the drawings.

[Example 1]
[Outline of vane pump]
FIG. 1 is an axial sectional view of the variable displacement vane pump 1 (II sectional view of FIG. 2). FIG. 2 is a radial cross-sectional view (II-II cross-sectional view of FIG. 1) of the variable displacement vane pump 1. FIG. 2 shows the case where the cam ring 4 is located most in the negative direction of the y-axis (maximum eccentricity).
The variable displacement vane pump 1 of the first embodiment supplies hydraulic oil to a power steering device mounted on a vehicle, and a drive shaft 2 is connected to a pulley 9 driven via a belt or the like by an engine (not shown). Has been done. The cross-sectional view of FIG. 2 schematically shows an oil passage configuration and the like in order to simplify the description of the pump function. The axial direction of the drive shaft 2 is the x-axis, and the direction in which the drive shaft is inserted into the pump housing 10 is the positive direction. The axial direction of the cam spring 201 (see FIG. 2) that restricts the swing of the cam ring 4 and the direction of urging the cam ring 4 is the y-axis negative direction, and the axis perpendicular to the x and y axes is the suction passage. The IN side is the z-axis positive direction. The vane pump of the first embodiment boosts the working oil sucked from a reservoir tank (not shown) to a required pressure and supplies a required flow rate to the power steering device.

The variable displacement vane pump 1 has a drive shaft 2, a rotor 3, a cam ring 4, an adapter ring 5, and a pump housing 10. The drive shaft 2 is rotatably supported by the pump housing 10. A pulley 9 is connected to an end of the drive shaft 2 on the negative side of the x-axis via a boss member 24. The pulley 9 is connected to the engine via a belt or the like, and the variable displacement vane pump 1 is driven by the driving force of the engine. The rotor 3 is a rotating body that is rotationally driven by the drive shaft 2, and a plurality of slits 31 that are axial grooves are radially formed on the outer periphery of the rotor 3. A plate-shaped vane 32 having substantially the same length in the x-axis direction as that of the rotor 3 is inserted into each of the slits 31 so as to be capable of advancing and retracting in the radial direction. A back pressure chamber 33 is provided at the inner diameter side end of each slit 31, and hydraulic oil is supplied to urge the vanes 32 radially outward. The rotor 3, the cam ring 4, and the vanes 32 form a pump element.

The pump housing 10 is formed of a front housing 11 and a rear housing 12. The front housing 11 has a bottomed cup shape that opens toward the positive direction of the x-axis, and a tubular pump element accommodating portion 112 is formed on the inner peripheral portion of the front housing 11. The negative side of the pump element housing portion 112 in the x-axis direction is closed by a bottom portion 111. A disk-shaped pressure plate 6 is housed in the bottom portion 111. The front housing 11 and the rear housing 12 are fastened and fixed by a plurality of bolts. Inside the pump element accommodating portion 112, the adapter ring 5, the cam ring 4, and the rotor 3 are accommodated on the positive side of the pressure plate 6 in the x-axis direction. The rear housing 12 is in liquid-tight contact with the adapter ring 5, the cam ring 4 and the rotor 3 in the positive x-axis direction, and the adapter ring 5, the cam ring 4 and the rotor 3 are sandwiched between the pressure plate 6 and the rear housing 12.

The adapter ring 5 is an annular member that is provided inside the pump element housing portion 112 that is a tubular portion, and has the cam ring housing portion 54 formed therein. The shape of the adapter ring 5 is not limited to a ring shape and may be a C-shape as long as it has at least an arc-shaped portion so that a storage space is formed inside. A radial through hole 51 is provided at the y-axis positive direction end of the adapter ring 5. Further, a plug member insertion hole 114 is provided at the end portion of the front housing 11 in the positive direction of the y-axis, and a bottomed cup-shaped plug member 73 is inserted to secure liquid tightness between the front housing 11 and the outside. A cam spring 201 is inserted in the inner periphery of the plug member 73 so as to be capable of expanding and contracting in the y-axis direction, penetrates the radial through hole 51 of the adapter ring 5 and contacts the cam ring 4, and biases in the y-axis negative direction. .. The cam spring 201 biases the cam ring 4 in a direction in which the swing amount is maximum, and stabilizes the discharge amount (cam ring swing position) at the time of starting the pump in which the pressure is not stable.

A cam ring (4) is provided inside the cam ring housing (54) so as to be movable with respect to the drive shaft (2), and a plurality of pump chambers (13) are formed together with the rotor (3) and the vanes (32). The cam ring 4 is an annular member that is movably provided in the cam ring housing portion 54 of the adapter ring 5 and has an axial length shorter than the axial length of the adapter ring 5.
A pin 40a is provided between the adapter ring 5 and the cam ring 4. The pin 40a prevents the adapter ring 5 from rotating in the front housing 11 when the pump is driven.

A seal member 50 is provided at the z-axis positive direction end of the adapter ring inner peripheral surface 53, a support surface N is formed at the z-axis negative direction end, and a support plate 40 is provided at the support surface N. .. The support plate 40 and the seal member 50 separate the first fluid pressure chamber A1 and the second fluid pressure chamber A2 between the cam ring 4 and the adapter ring 5. The first fluid pressure chamber A1 is provided inside the cam ring housing portion 54 and on the outer peripheral side of the cam ring 4, and when the cam ring 4 moves in the direction in which the volumes of the plurality of pump chambers 13 increase, the internal volume decreases. Formed on the side. The second fluid pressure chamber A2 is provided inside the cam ring housing portion 54 and on the outer peripheral side of the cam ring 4, and the side where the internal volume increases when the cam ring 4 moves in the direction in which the volumes of the plurality of pump chambers 13 increase. Is formed in. The cam ring 4 is provided on the support plate 40 so as to be swingable in the y-axis direction.
A through hole 52 is provided on the z-axis positive direction side of the adapter ring 5 and on the y-axis negative direction side of the seal member 50. The through holes 52 communicate with the spool 70 via control pressure oil passages 113 provided in the front housing 11, respectively, and connect the first fluid pressure chamber A1 on the y-axis negative direction side and the spool 70.

[Front housing configuration]
A drive shaft through hole 117 is formed in the front housing 11 from the bottom 111 of the pump element housing 112 to the outside. The drive shaft through hole 117 is formed with a shaft insertion portion 117b adjacent to the opening 117a opening to the bottom 111 and having a diameter larger than that of the opening 117a. Further, a seal member holding portion 117c communicating with the shaft inserting portion 117b and having a diameter larger than that of the shaft inserting portion 117b is formed. The seal member 15 is held by the seal member holding portion 117c. The seal member 15 is formed in an annular shape so as to slide on the outer periphery of the drive shaft 2, and seals liquid-tight so that the hydraulic fluid in the pump element housing portion 112 does not leak to the outside.
Adjacent to the seal member holding portion 117c, a bearing holding portion 117d having a diameter larger than that of the seal member holding portion 117c is formed. The ball bearing 16 is held by the bearing holding portion 117c. The outer race of the ball bearing 16 is restricted in its movement in the positive x-axis direction by the bottom of the bearing holding portion 117c, and restricted in its movement in the negative x-axis direction by the snap ring 17.

The opening of the drive shaft through hole 117 on the negative side of the x-axis is closed by the cover member 18. On the x-axis negative direction side of the front housing 11, a tubular portion 119 that is normally formed so as to surround the opening of the drive shaft through hole 117 is formed. The cover member 18 is fixed by press-fitting the inner peripheral surface thereof into the tubular portion 119. Concave groove portions 119a are formed at two locations on the outer periphery of the cylindrical portion 119 in parallel with the axial direction of the drive shaft 2. The groove portions 119a are arranged at approximately 180° apart (at equal intervals). A seal member 19 is held by the cover member 18. The seal member 19 is formed in an annular shape so as to slide on the outer periphery of the drive shaft 2, and liquid-tightly seals so that muddy water or the like from the outside does not enter the inside. The structure of the cover member 18 will be described in detail later.

A control valve accommodating hole 116 for accommodating the spool 70, which is a pressure control means for controlling the eccentric amount of the cam ring 4 by controlling the pressure in the first fluid pressure chamber A1, is provided on the z-axis positive direction side of the front housing 11. A control valve suction oil passage 115 for introducing the hydraulic oil from the suction passage IN to the spool 70 and a control pressure oil passage 113 for discharging the control pressure into the first fluid pressure chamber A1.
Further, in the bottom portion 111, a suction groove 111b formed by being recessed at a position facing a second suction port 62 of the pressure plate 6 described later, and a discharge groove 111a connected to the discharge groove 111a for discharging hydraulic oil to the power steering device. And passage 20. The suction pressure acts on the suction groove 111b, and the discharge pressure acts on the discharge groove 111a and the discharge pressure introduction groove 111c.

[Structure of pressure plate]
The pressure plate 6 is provided inside the pump element accommodating portion 112 that is a tubular portion, and is arranged between the adapter ring 5 and the bottom portion 111. Further, the pressure plate 6 is a hole portion formed so that the drive shaft 2 can penetrate therethrough, and a through hole 66 formed so as to be relatively movable in the axial direction with respect to the drive shaft 2.
On the side surface 61 on the positive side of the x-axis of the pressure plate 6, there are provided a second suction port 62 arranged in a circular shape on the positive side of the z-axis and a second discharge port 63 arranged on a negative side of the z-axis in a circular shape. And a suction side back pressure groove 64 and a discharge side back pressure groove 65 for introducing a discharge pressure into the back pressure chamber 33. The second suction port 62 is arranged so as to face one axial end surface of the cam ring 4, and is formed so as to open in a suction region where the volumes of the plurality of pump chambers 13 increase as the drive shaft 2 rotates. ..
Further, the pressure plate 6 is biased toward the adapter ring 5 side by the discharge pressure of the discharge groove 111a acting on the side surface 67 in the x-axis negative direction.

[Rear housing configuration]
In the rear housing 12, a suction passage 12a for introducing the working oil from a reservoir tank (not shown) that stores the working oil into the first suction port 122 is formed in the z-axis direction. An oil passage 12d for supplying hydraulic oil to the spool 70 is formed on the z-axis positive direction side of the suction passage 12a. A bottomed shaft support portion 12c that supports the drive shaft 2 via a bush 14 is formed in a substantially central portion of the rear housing 12. A lubricating oil passage 12b communicating with the shaft supporting portion 12c is formed at the lower end of the suction passage 12a to ensure lubricity in sliding between the drive shaft 2 and the shaft supporting portion 12c.
On the negative side of the rear housing 12 in the x-axis direction, there is a pump forming surface 120 that is raised in a circular shape. On the pump forming surface 120, a first suction port 122 is formed so as to face one end surface of the cam ring 4 in the axial direction and to open to a suction region. A first discharge port 123 is formed so as to face one end surface of the cam ring 4 in the axial direction and to open in the discharge region. A suction side back pressure groove 124 and a discharge side back pressure groove 125 for introducing a discharge pressure into the back pressure chamber 33 are formed on the pump forming surface 120.

[Configuration of control unit]
The control unit of the variable displacement vane pump 1 includes a first fluid pressure chamber A1, a second fluid pressure chamber A2, a control valve 7 and a discharge passage 20.
The discharge passage 20 is a passage for hydraulic oil that connects the respective parts within the pump housing 10. The front housing 11 is formed with a substantially cylindrical control valve accommodation hole 116 extending in the y-axis direction, and the control valve 7 is accommodated in the control valve accommodation hole 116.
The control valve 7 switches the position of the spool 70 to switch the supply of hydraulic oil to the first fluid pressure chamber A1. In the state of FIG. 2, the control pressure oil passage 113 and the low pressure chamber 116b described later are in communication with each other, and the suction pressure acts on the first fluid pressure chamber A1. A valve spring 71 is installed in a compressed state on the y-axis positive direction side of the spool 70, and always urges the spool 70 to the y-axis negative direction side. A lid member 72 that closes the opening of the control valve housing hole 116 is screwed onto the spool 70 on the negative side in the y-axis direction.
The spool 70 has a first small diameter portion 70a, a first land portion 70b, a second small diameter portion 70c, and a second land portion 70d formed in order from the y-axis negative direction side. The outer diameters of the first land portion 70b and the second land portion 70d are formed to be substantially the same as the inner diameter of the control valve accommodation hole 116, and the outer diameters of the first small diameter portion 70a and the second small diameter portion 70c are controlled. The diameter is smaller than the inner diameter of the valve accommodating hole 116. Inside the control valve accommodation hole 116, a high pressure chamber 116a is formed by a space surrounded by the inner periphery of the control valve accommodation hole 116, the outer periphery of the first small diameter portion 70a, the lid member 72, and the first land portion 70b. Further, a low pressure chamber 116b is formed by a space surrounded by the inner circumference of the control valve accommodating hole 116, the outer circumference of the second small diameter portion 70c, the first land portion 70b, and the second land portion 70d. Further, a medium pressure chamber 116c is formed by the inner periphery of the control valve accommodating hole 116, the y-axis positive direction side end surface, and the second land portion 70d.

Both the high pressure chamber 116a and the medium pressure chamber 116c communicate with the discharge passage 20. The discharge passage 20 communicates with the discharge groove 111a and branches into a passage 21 and a passage 22. The passage 21 is connected to the high pressure chamber 116a, and the passage 22 is connected to the medium pressure chamber 116c. A metering orifice 23 is provided in the passage 22. As the discharge flow rate of the variable displacement vane pump 1 increases due to the metering orifice 23, the differential pressure across the metering orifice 23 increases. That is, as the discharge pressure becomes higher, the oil pressure in the medium pressure chamber 116c becomes lower than the oil pressure in the high pressure chamber 116a.
Inside the spool 70, a relief valve accommodating hole 70e that is open on the y-axis positive direction side is formed. The relief valve 8 is housed in the relief valve housing hole 70e. The relief valve 8 connects the intermediate pressure chamber 116c and the low pressure chamber 116b when the hydraulic pressure in the intermediate pressure chamber 116c becomes too high. The relief valve 8 is provided with a valve spring 80, a spring holding member 81, a ball plug 82, and a seat member 83 in order from the y-axis negative direction side. The seat member 83 is formed with a through hole 83a penetrating in the axial direction, and is press fitted into the relief valve accommodating hole 70e. The valve spring 80 is provided in a compressed state between the bottom surface of the relief valve accommodating hole 70e on the negative side in the y-axis direction and the spring holding member 81, and the ball plug 82 and the seat member 83 are interposed via the spring holding member 81. Biased in the direction. A through hole 70f is formed in the spool 70 near the position where the ball plug 82 is located so as to penetrate the relief valve housing hole 70e and the outer periphery of the second small diameter portion 70c. That is, the y-axis negative direction side of the relief valve accommodation hole 70e from the ball plug 82 communicates with the low pressure chamber 116b.

[Structure of cover member]
FIG. 3 is a sectional view of the cover member 18 as a single product. The cover member 18 surrounding the tip of the tubular portion 119 of the front housing 11 is formed by forging from a metal material and is provided with a bottom portion 18c having a step portion 18g on the inside in the radial direction provided so as to face the opening portion of the front housing 11 and a tubular portion. The press-fitted portion 18a, the through hole 18b, the seal holding portion 18d, and the extending portion 18e extending in the x-axis direction are formed. After that, only the inside of the bent portion 18f connecting the bottom portion 18c and the tubular press-fitted portion 18a and the inner peripheral side of the press-fitted portion 18a are formed by machining. The press-fitted portion 18a is molded in a direction in which the radial dimension, which is the distance between the inner peripheral surface of the press-fitted portion 18a and the rotation center axis of the drive shaft 2, separates from the bent portion 18f (rightward in the drawing). It is shaped into an inverse taper that gradually decreases toward the end (α<90°).
Further, the radius of curvature r3 of the outer circumference of the bent portion 18f is formed so that the radius of curvature r1 of the inner circumference is smaller, and a chamfer C1 is formed on the inner circumference side of the open end of the press-fitted portion 18a.

[Configuration near the cover member]
FIG. 4 is an enlarged view of the vicinity of the cover member 18. In the outer peripheral portion of the cover member 18, the inner periphery of the press-fitted portion 18a extending in the positive direction of the x-axis overlaps the outer periphery of the tubular portion 119 of the front housing 11 with the ball bearing 16 in the x-axis direction (shown by d). It is press-fit to do.
The outer peripheral surface of the tubular portion 119 has the same diameter or has a slight draft.
In addition, except for the non-contact surface of the chamfer C1 portion of the outer peripheral corner of the opening side of the tubular portion 119 and the tip inner peripheral chamfer C2 portion of the press-fitted portion 18a, all the non-contact surfaces are tightened. Will have a teenager.
The end of the groove 119a is formed so as to open to the outside when the cover member 18 is press-fitted. A through hole 18b through which the drive shaft 2 penetrates is formed in the central portion of the cover member 18. A bottom portion 18c having a step portion 18g protruding in the negative direction of the x-axis is formed on the way from the press-fitted portion 18a to the through hole 18b. The step portion 18g of the bottom portion 18c is inserted into the inner peripheral side of a recessed portion 24a formed in a recessed shape on the side surface of the boss member 24 in the positive x-axis direction. As a result, the passage from the outside to the seal member 19 has a labyrinth structure. A seal holding portion 18d having an inner diameter capable of holding the seal member 19 is formed on the side surface of the cover member 18 on the x-axis positive direction side. An extension portion 18e extending in the positive direction of the x-axis is formed on the side surface of the seal holding portion 18d. The tip of the extending portion 18e on the ball bearing 16 side is inserted between the outer race and the inner race of the ball bearing 16. In other words, the rotor 3 side (x-axis positive direction side) of the seal holding portion 18d is located closer to the rotor 3 side than the end surface of the ball bearing 16.
The outer diameter of the end portion (tip portion 2b) of the drive shaft 2 on the x-axis negative direction side of the ball bearing 16 is smaller than the outer diameter of the bearing installation portion 2a where the ball bearing 16 is provided (φa> φb).
FIG. 5 is an enlarged view of a main part near the cover member. The corners of the front housing 11 on the side of the opening of the tubular portion 119 are chamfered C2 and C3 on both the inner and outer circumferences. Note that the radius of curvature r1 inside the bent portion 18f is smaller than the chamfer C2 on the outer peripheral corner of the tubular portion 119 (C2> r1).

[effect]
The effects obtained in Example 1 are listed below.

(1) The cover member 18 that surrounds the tip of the tubular portion 119 of the front housing 11 is formed by forging from a metal material, and the bottom portion 18c provided to face the opening of the front housing 11 and the tubular press-fitted portion. 18a is formed. After that, only the inside of the bent portion 18f connecting the bottom portion 18c and the cylindrical press-fitted portion 18a and the inner peripheral side of the press-fitted portion 18a are machined. The press-fitted portion 18a is formed in a direction in which the radial dimension, which is the distance between the inner peripheral surface of the press-fitted portion 18a and the rotation center axis of the drive shaft 2, moves away from the bent portion 18f (rightward in the drawing). Then, the taper is shaped into an inversely tapered shape (α<90°).
Therefore, the tightening margin with the tubular portion 119 of the front housing 11 becomes smaller on the side closer to the bent portion 18f, and the stress concentration on the bent portion 18f can be relaxed.

(2) Since the outer side surface of the bent portion 18f is not machined, it is possible to suppress the strength reduction of the bent portion 18f.
(3) Since the radius of curvature r1 inside the bent portion 18f is smaller than the chamfer C2 on the outer peripheral side corner of the tubular portion 119 (C2> r1), the inside of the bent portion 18f and the cylinder of the front housing 11 are Since the curved portion 119 can be separated from the curved portion 119 and the tightening margin of the bent portion 18f is eliminated, the stress concentration of the bent portion 18f can be further alleviated.
Further, except the inner peripheral side chamfer C1 at the open end of the press-fitted portion 18a and the outer peripheral side corner chamfer C2 of the tubular portion 119, all are press-fitting surfaces, so that the press-fitting load can be maintained and stabilized.
(4) By making the inner radius of curvature r1 of the bent portion 18f smaller than the outer radius of curvature r3, the outer bending of the bent portion 18f becomes gentle, and it is possible to further suppress the strength reduction of the bent portion 18f. it can.
(5) Except for the non-contact surfaces of the chamfered C2 portion of the outer peripheral corner of the opening of the tubular portion 119 and the inner peripheral chamfered C1 portion of the open end of the press-fitted portion 18a, both non-contact surfaces By having the interference between all the surfaces, the holding force of the cover member 18 can be improved.
(6) In the outer peripheral portion of the cover member 18, the inner periphery of the press-fitted portion 18a extending in the positive x-axis direction overlaps the outer periphery of the tubular portion 119 of the front housing 11 with the ball bearing 16 in the X-axis direction. Since the tubular portion 119 of the front housing 11 is sandwiched between the press-fitted portion 18a and the ball bearing 16, the tubular portion 119 is deformed to concentrate the stress on the bent portion 18f. Can be further alleviated.
(7) The cover member 18 is press-fitted into the front housing 11, and a seal member 19 seals between the cover member 18 and the drive shaft 2. Therefore, when the cover member 18 is press-fitted into the front housing 11, the air pressure inside the variable displacement vane pump 1 becomes high and the cover member 18 may be detached.
Therefore, in the first embodiment, the groove 119a is provided in the tubular portion 119 of the front housing 11 in the axial direction of the drive shaft 2.
Therefore, when the cover member 18 is press-fitted into the front housing 11, the internal air is released from the groove portion 119a, and the detachment of the cover member 18 can be suppressed.
There is a possibility that the air pressure inside the variable displacement vane pump 1 becomes high and the air pressure becomes high, and the cover member 18 comes off.
Therefore, in the first embodiment, the end of the groove 119a is formed so as to open to the outside when the cover member 18 is press-fitted.
Therefore, even if the temperature of the air inside the variable displacement vane pump 1 becomes high, the air can escape from the opening of the groove 119a and the detachment of the cover member 18 can be suppressed.
(8) When the cover member 18 is inserted into the tubular portion 119, if the air is not evenly released from the groove portion 119a, the pressure balance in the circumferential direction becomes uneven, and the cover member 18 tilts in the falling direction to perform the assembling work. There was a risk that the sex would deteriorate.
Therefore, in the first embodiment, the groove portions 119a are provided at equal intervals in the rotation direction of the drive shaft 2.
Therefore, when the cover member 18 is press-fitted into the tubular portion 119, the way air escapes from the groove portion 119a becomes uniform, and the pressure balance in the circumferential direction becomes uniform, so that the inclination of the cover member 18 in the tilting direction is suppressed. The workability of assembling can be improved.
When a large amount of muddy water entered, there was a risk that the seal member 19 could not sufficiently secure the sealing property.
Therefore, in the first embodiment, the path between the cover member 18 and the pulley 9 has a labyrinth structure in which the passage is bent halfway.
Therefore, it is possible to prevent the muddy water from entering at once and to secure the sealing property of the seal member 19.
(9) By providing the cover member 18, the axial length of the variable displacement vane pump 1 is increased.
Therefore, in the first embodiment, in the state where the press-fitted portion 19a is press-fitted into the tubular portion 119, the end portion of the cover member 18 on the ball bearing 16 side (the extending portion 18e of the seal holding portion 18d) is positioned more than the end surface of the ball bearing 16. I tried to get inside.
Therefore, the axial dimension of the variable displacement vane pump 1 can be reduced.
The ball bearing 16 is inserted into the pump housing 10 after being attached from the end of the drive shaft 2 on the negative side of the x-axis, but the surface of the drive shaft 2 is damaged when the ball bearing 16 is inserted into the drive shaft 2. There was a fear. If the portion of the drive shaft 2 that contacts the seal member 19 is damaged, the seal lip may be damaged and the sealing performance may be deteriorated.
Therefore, in Example 1, the outer diameter of the portion of the drive shaft 2 that contacts the ball bearing 16 is smaller than the outer diameter of the portion that contacts the seal member 19.
Therefore, it is possible to prevent the seal lip from being damaged and ensure the sealing property.

[Other Embodiments]
As described above, the mode for realizing the present invention has been described based on the embodiments, but the specific configuration of the present invention is not limited to the embodiments, and design changes within the scope not departing from the gist of the invention. Etc. are included in the present invention. For example, the corners on the opening side of the tubular portion 119 of the front housing 11 are chamfered C2 and C3 on both the inner and outer circumferences, but they may be R portions having a radius of curvature. Further, the variable displacement pump has been described, but the invention can be applied to a fixed displacement pump.

2 Drive shaft 3 Rotor (pump element)
4 Cam ring (pump element)
9 Pulley (rotational force transmission part)
10 Pump Housing 11 Front Housing (Pump Housing)
16 ball bearings
18 cover member 18a press-fitted portion 18f bent portion 19 seal member 24 boss member (rotational force transmission portion)
32 vanes (pump element)
112 Pump Element Housing 117 Drive Shaft Through Hole 119a Cylindrical Section

Claims (6)

The pump device is
A pump housing having a pump element housing therein, a drive shaft through hole provided in the pump housing, communicating with the pump element housing, and formed to open to the outside of the pump housing, and the drive shaft penetrating hole. A tubular portion formed in the pump housing so as to surround the open end of the hole;
A drive shaft that is inserted into the drive shaft through hole such that one end side projects to the outside of the open end of the drive shaft through hole, and is supported by the pump housing.
A bearing that is provided in an annular space between the inner peripheral side of the drive shaft through hole and the drive shaft and rotatably supports the drive shaft with respect to the pump housing;
A rotational force transmitting portion that is provided on the one end side of the drive shaft and that transmits a rotational force from an external power source to the drive shaft;
When the direction of the rotary shaft of the drive shaft is the axial direction, a bottom portion provided between the bearing and the rotational force transmitting portion in the axial direction and provided to face the opening end, and a bottom portion of the bottom portion. A cover member having a press-fitted portion that is provided in a tubular shape in the axial direction continuously from a radially outer end through a bent portion, and a through hole that is provided in the bottom portion and into which the drive shaft is inserted,
A sealing member which is provided on the bottom portion and liquid-tightly seals between the bottom portion and the drive shaft,
A forging step of forming the bottom portion and the press-fitted portion of the cover member by forging from a metal material;
A step of molding the inside of the bent portion between the bottom portion and the press-fitted portion and the inner peripheral side of the press-fitted portion by machining, between the inner peripheral surface of the press-fitted portion and the rotation center axis of the drive shaft. A cutting step of molding the inner peripheral surface of the press-fitted portion such that the radial dimension which is the distance becomes gradually smaller in the direction away from the bent portion side,
A cover member mounting step of mounting the cover member on the tubular portion by press-fitting the tubular portion into the press-fitted portion;
A method for manufacturing a pump device, comprising: The method for manufacturing a pump device according to claim 1,
A method for manufacturing a pump device, wherein an outer surface of the bent portion is not machined. The method for manufacturing a pump device according to claim 1,
Manufacturing the pump device, characterized in that the cutting step is a step of forming the inner radius of curvature of the bent portion to be smaller than the radius of curvature of the corner of the tubular portion facing the bent portion. Method. The method for manufacturing a pump device according to claim 3,
The method of manufacturing a pump device, wherein the cutting step is a step of forming the inner radius of curvature of the bent portion to be smaller than the outer radius of curvature of the bent portion. The cutting step in the manufacturing method of the pump apparatus according to claim 1, wherein among the inner peripheral surface of the press-fit portion, opposite ends of the bottom side in the axial direction of the drive shaft and the bottom side of the end portion Forming a contact surface that is provided between each of the end portions on the side and that is provided between a pair of non-contact surfaces that do not contact the outer peripheral surface of the tubular portion and that contacts the outer peripheral surface of the tubular portion. hand,
The method for manufacturing a pump device, wherein the contact surface is formed so as to have an interference with the outer peripheral surface of the tubular portion over the entire contact surface. The method for manufacturing a pump device according to claim 5,
The method for manufacturing a pump device, wherein the contact surface is provided so as to overlap the bearing in the axial direction of the drive shaft.

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