JPH0746785Y2 - Vane pump - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to a vane pump, and more specifically, it is provided between each vane and the bottom of each storage groove in order to press the vane against the inner peripheral surface of the cam ring. The present invention relates to a vane pump including a rotor having a coil spring interposed therein.

[Prior art]

As is well known, the rotor of the vane pump has a plurality of storage grooves each having a radial direction in a depth direction in a cylindrical main body portion.
They are evenly arranged in the circumferential direction and are formed over the entire length in the axial direction, and vanes each having a rectangular flat plate shape are slidably inserted into each of these storage grooves. The vane pump is configured by fitting the rotor coaxially and rotatably in a casing having a cam ring having an uneven wall thickness, and pumps a space formed between the outer circumference of the rotor body and the inner circumference of the cam ring. Is designed to operate as a chamber, and the oil introduced into the pump chamber is
The pressure is increased by sealing between two vanes adjacent to each other and rotating as the rotor rotates. Therefore, in the vane pump, it is important that each vane of the rotor is surely pressed against the inner peripheral surface of the cam ring to ensure the above-mentioned sealing, and between each vane and the bottom of each storage groove. A biasing means is provided for biasing this radially outward, and a coil spring is generally used as the biasing means.

FIG. 5 is an enlarged view of a main part of a conventional vane pump, and FIG. 6 is a cross-sectional view taken along the line VI-VI of FIG. 5, both showing a mounted state of a vane urging coil spring.

In the figure, reference numeral 30 denotes a cylindrical rotor body, which is coaxially fitted in a cam ring 31 having an eccentric cylindrical shape. As described above, the rotor body 30 has a plurality of storage grooves 30b, 30
B (only one is shown in FIG. 5) are formed, and vanes 30a having a rectangular flat plate shape are slidably inserted along the storage grooves 30b. Coil springs 30c for urging the vanes 30a are provided on both sides of each vane 30a in the width direction, and these have locking holes formed at one end in the longitudinal direction at the bottom of the storage groove 30b, as shown in FIG. Lock each with 30e,
Further, the other end is provided with notches 30d, 3 formed in the base of the vane 30a.
They are interposed between the vane 30a and the storage groove 30b in a state of being locked to 0d respectively.

Now, the storage groove 30b can be formed at the same time when the rotor body 30 is sintered and molded, but the locking hole 30e at the bottom of the storage groove 30b is
Due to the formation mode, the rotor body 30 must be formed by machining after the formation. However, this processing has to be performed through the narrow-width storage groove 30b, and each of the plurality of storage grooves 30b, 30b ... requires two locking holes 30e, 30e, which is considerable for the entire rotor. However, there is a problem that a great number of processing man-hours are required to correctly form all of the locking holes 30e, 30e ... With sufficient accuracy. Further, at the time of assembling the rotor, a work of correctly locking one end of the coil spring 30c inserted through the narrow gap between the both side walls of the storage groove 30b in the locking hole 30e, and
There is a problem that a complicated work such as a work of inserting the vane 30a into the storage groove 30b while inserting the other end of the coil spring 30c into the cutout portion 30d is required, which requires a great number of assembling steps.

In order to solve the above-mentioned difficulties, one of the applicants of the present application proposed in Japanese Patent Application No. 62-325977 a vane pump capable of easily and surely mounting a vane biasing coil spring. FIG. 7 is a sectional view showing a mounted state of the vane urging coil spring in the present invention.

The vane pump according to the present invention bends a thin and thin plate material in the thickness direction of the vane pump as shown in the drawing, and provides a pair of sandwiching portions 60, 60 projecting to one side in the thickness direction at both ends in the longitudinal direction, By using the spring holding member 6 in which the pair of fitting portions 61, 61 projecting to the other side are provided at the positions distributed from the center in the longitudinal direction to both sides, the above-mentioned difficulties are solved. The spring holding member 6 stores the vanes 30a from the protruding side of the holding portions 60, 60 with the coil springs 30c, 30c for urging the vanes 30a fitted onto the fitting portions 61, 61 respectively. The rotor main body 30 is inserted into the groove and held by the holding parts 60, 60.
By holding both sides in the width direction of the
It is fixed to the bottom of the storage groove of the vane 30a.

When this spring holding member 6 is used, the formation of the locking hole 30e in FIG. 6 is unnecessary, and the work of fitting the coil springs 30c, 30c onto the fitting portions 61, 61 is performed by the spring holding member 6 Since it can be performed before mounting, the number of processing steps and assembling steps of the rotor can be significantly reduced, and the coil springs 30c and 30c can be securely fixed.

[Problems to be solved by the device]

However, in the spring holding member 6 shown in FIG. 7, when manufacturing the spring holding member 6, defects such as cracks may occur at the bent portions of the tips of the fitting portions 61, 61, which leads to a decrease in yield. After manufacturing this, the springback of the bent portion may cause the root portions of the fitting portions 61, 61 to gradually expand, and the coil springs 30c, 30c externally fitted to the fitting portions 61, 61 may be expanded.
However, there is a problem that the expansion and contraction operation of the vanes is hindered, which causes a problem in the advancing and retracting operation of the vanes 30a, 30a ... After assembling.

Further, when the coil spring 30c is fitted into the fitting portion 61 and is held by the fitting portion 61, the expansion and contraction operation of the coil spring 30c is not hindered, and the coil spring 30c does not fall off the fitting portion 61. It is required to realize a proper fitting state between the two members so that there is no fear of this, but this realization is difficult in the spring holding member 6 having the above-described configuration, and the fitting is required each time the fitting is performed. Joint part 61
There is a problem that it is necessary to correct the shape.

The present invention has been made in view of such circumstances, and it is possible to reliably and easily mount the coil spring for biasing the vane, and the expansion and contraction operation of the coil spring after mounting can be hindered. It is an object of the present invention to provide a vane pump that does not have a risk of falling off of a coil spring.

[Means for Solving the Problems]

In the vane pump according to the present invention, a vane slidably inserted along each of the plurality of storage grooves formed on the peripheral surface of the cylindrical body is interposed between the storage groove bottom and each of the storage grooves. In a vane pump provided with a rotor that is biased outward in the radial direction by a mounted coil spring, a holding rod for externally fitting and holding the coil spring is provided upright on a part of the holding rod, and the bottom of each of the storage grooves is provided. A spring holding member fixed across the annular groove for fluid flow formed on both ends of the rotor in the axial direction in a manner of communicating with each other, wherein the holding rod is a shaft end of the storage groove on the bottom side. Has a reduced diameter portion that reduces its diameter toward the shaft end side, and the coil spring has a small diameter seat portion having a smaller diameter than the other shaft end portion on the one shaft end side, and the small diameter seat portion has the reduced diameter portion. It is characterized by being fitted in.

[Operation] The spring holding member is fixed across the annular groove. The coil spring is externally fitted to the holding rod of the spring holding member, and the small-diameter seat portion is fitted to the reduced-diameter portion. Therefore, the coil spring can be easily mounted, and the fitting is surely performed, and the pump is operated. Sometimes it does not fall out. Further, since the holding rod does not deform with time unlike the conventional fitting portion 61, the holding and expanding / contracting operation of the coil spring is not hindered.

〔Example〕

Hereinafter, the present invention will be described in detail with reference to the drawings showing an embodiment thereof. FIG. 1 is a vertical sectional view showing a main part of a drive connecting device for a four-wheel drive vehicle constructed by using a vane pump according to the present invention, and FIG. 2 is an enlarged front sectional view taken along line II-II of FIG. Is.

The drive coupling device shown in FIGS. 1 and 2 transmits the driving force from the front wheels to the rear wheels or from the rear wheels to the front wheels in accordance with the rotational speed difference between the front and rear wheels. A vane pump 3 comprising a rotor whose rotation is restricted by an input shaft 1 which rotates in conjunction with one of the front and rear wheels, and a casing whose rotation is restricted by an output shaft 2 which rotates in conjunction with the other of the front and rear wheels. The oil tank T to be stored, and the suction oil passage and the discharge oil passage of the vane pump 3 are integrally configured. In a four-wheel drive vehicle configured to directly transmit the driving force from the engine to the front two wheels, this drive coupling device is used by being mounted in the middle of a propeller shaft that couples the front and rear wheels. In this case, the input shaft 1 corresponds to the front wheel side portion of the propeller shaft, and the output shaft 2 also corresponds to the rear wheel side portion.

The casing of the vane pump 3 includes a cam ring 31 having an eccentric thickness cylindrical shape, a side plate 32 having a hollow disk shape and a side plate 32 having a hollow disk shape that holds the cam ring 31 from both sides in the axial direction. Plate 33 and side plate
The cam ring 31 of 32 and a cylindrical shaft sealing member 34 that is flange-fixed on the opposite side are formed in the side plate 33 by penetrating the flange portion of the shaft sealing member 34, the side plate 32, and the cam ring 31 in this order. A plurality of fixing bolts 35, 35, which are screwed into the different screw holes, are coaxially integrated. This casing includes a connecting flange 20 formed at the end of the output shaft 2 and a plurality of fixing bolts 21, 21.
, And is fixed coaxially to the output shaft 2 by being fixed to the outer surface of the side plate 33.
It rotates around its axis in conjunction with the rotation of. A part of the outer surface of the casing is fitted on the outer peripheral surface of the side plate 33 and the outer peripheral surface of the shaft sealing member 34 to surround the outer sides of the cam ring 31 and the side plates 32, 33 as shown in FIG. In the embodiment, the thin-walled tubular surrounding member 38 is fitted, and the working oil of the vane pump 3 is the inner circumference of the surrounding member 38,
It is enclosed in an oil tank T formed in an annular shape with the outer circumference of the casing.

On the other hand, the rotor of the vane pump 3 has a plurality of flat plate-shaped vanes 30a, 30a ...
It is configured so as to be slidable in the radial direction as will be described later. The rotor shaft 36, which is the rotating shaft of the rotor 3, has a needle roller bearing 32a that is internally fitted and fixed to the hollow portion of the side plate 32.
And a ball bearing 33a that is internally fitted and fixed to the hollow portion of the side plate 33 and is located on the shaft center of the casing.
It is fitted to the outside and is splined to this. The inner circumference of the cam ring 31 is formed in a circle having a diameter slightly larger than the outer circumference of the rotor body 30, and a plurality of recesses (three in this embodiment) are formed in a substantially equal distribution, as shown in FIG. The rotor main body 30 having such an axial cross-sectional shape and mounted on the rotor shaft 36 as described above is fitted inside the cam ring 31 in such a manner that both sides are held by the side plates 32, 33, and the rotor main body 30 is inserted. Between the outer peripheral surface of 30 and the inner peripheral surface of the cam ring 31, a pump having a modified crescent-shaped axial cross-section is surrounded by the both surfaces and the side surfaces of the side plates 32, 33 at the position where the recess is formed. Chamber 4
0,40,40 are formed.

The outer circumference of the rotor shaft 36 is sealed by an oil seal 34a and an X ring 34b fitted and fixed to the shaft sealing member 34, and the rotor shaft 36 is projected to the outside of the shaft sealing member 34 by an appropriate length. The connecting flange 37 formed at the end of the input shaft 1 is connected to the connecting flange 10 formed at the end of the input shaft 1 by a plurality of fixing bolts 11,1.
It is fixed coaxially by 1. That is, the rotor of the vane pump 3 is coaxially connected to the input shaft 1 via the rotor shaft 36 and the connecting flanges 37 and 10, and rotates inside the casing in conjunction with the rotation of the input shaft 1. . Thus, when there is a difference in rotational speed between the input shaft 1 and the output shaft 2, a difference in rotational speed between the rotor interlocking with the former and the casing interlocking with the latter is generated. Relative rotation occurs.

In the rotor body 30, a plurality of storage grooves 30b, 30b ... Having a predetermined depth inward in the radial direction are evenly arranged in the circumferential direction and are formed over the entire length in the axial direction. The vane 30a having a rectangular flat plate shape is slidably inserted in the groove 30b along the wall surface of the storage groove 30b. A coil spring 30c is interposed between the bottom of the storage groove 30b and the base of the vane 30a. The vane 30a has an urging force of the coil spring 30c and the bottom of the storage groove 30b will be described later. By the pressure of the pressure oil thus introduced, an outward pressing force is applied in the radial direction of the rotor body 30.

Next, the structure of the suction oil passage and the discharge oil passage of the vane pump 3 will be described. Each of the pump chambers 40, 40, 40 has a pair of suction ports 40a, 40a located at both ends in the circumferential direction thereof and opening to the side plate 32 side, and a pair of discharge holes 40b opening to the side plate 33 side. , 40b are formed as shown in FIG. As shown in FIG. 1, each suction port 40a has a side plate 3
2, a suction check valve 41 that is installed in the pump chamber 40 and allows only an inflow into the pump chamber 40, and a suction hole that is formed by penetrating the flange portion of the shaft sealing member 34 in the axial direction in alignment with the mounting position of the suction check valve 41. And 42 to communicate with the oil tank T. Further, each of the discharge ports 40b is formed in a V shape and is folded back inward in the radial direction, and one end of a discharge hole 44 formed in the side plate 33 is opened. The bottoms of the respective vanes 30a, 30a ... Respective storage grooves 30b, 30b ... Are mutually connected to the side surface of the rotor body 30 via a discharge check valve 45 that is mounted midway and allows only the outflow from the pump chamber 40. It communicates with the annular groove 46 formed in the embodiment.
Further, the annular groove 46 communicates with the hollow portion of the side plates 32, 33 via a slight gap interposed between both side surfaces of the rotor body 30 and the side plates 32, 33.
Further, these hollow portions are communicated with the oil tank T outside the casing by a reflux hole 47 penetrating the shaft sealing member 34 in the radial direction or a reflux hole 48 penetrating the side plate 33 in the radial direction. That is, the suction oil passage of the vane pump 3 is constituted by the suction hole 42 and the suction check valve 41, and the discharge oil passage is formed by the discharge hole 44, the discharge check valve 45 in the middle thereof, and the storage groove 30b. , 30b ..., the gaps on both sides of the rotor body 30, and the return oil passages 47, 48.

In the drive coupling device including the vane pump 3 having the above-described configuration, the rotational speed difference between the front and rear wheels is increased during turning, acceleration / deceleration, or when one of the front and rear wheels is idling. When the vehicle is in a running state, a speed corresponding to the rotational speed difference is provided between the rotor rotating in conjunction with the front wheels via the input shaft 1 and the casing rotating in conjunction with the rear wheels via the output shaft 2. Relative rotation occurs. When the relative rotation occurs in this way, the oil in the oil tank T is introduced into each pump chamber 40 through the suction hole 42 and the suction check valve 41 from the suction port 40a located on the upstream side in the relative rotation direction. . This introduced oil is sealed between the adjacent vanes 30a and 30a, and the rotor body 3
Each pump chamber 4
0 Hydraulic pressure is generated inside. This generated oil pressure is
It acts between the outer peripheral surface of 0 and the inner wall surface of the pump chamber 40 in a direction to prevent the relative rotation, and thereby drives between the rotor and the casing, that is, between the input shaft 1 and the output shaft 2. Power is transmitted.

If the process of pressurization inside the pump chamber 40 is further detailed,
Part of the oil sealed between the adjacent vanes 30a, 30a passes through an extremely thin throttle hole 39 formed in the vicinity of the tip of the vane 30a in the thickness direction. Then, it leaks to the low pressure side (upstream side in the relative rotation direction) and is compressed again, while the remaining portion is the discharge port 40 located on the downstream side in the relative rotation direction.
From b, it is delivered to the discharge hole 44, and is introduced to the bottom of the storage grooves 30b, 30b ... Through the discharge hole 44, the discharge check valve 45, and the annular groove 46. The pressure oil applies a pressing force outward in the radial direction to the vanes 30a inserted in the respective storage grooves 30b, and leaks to the hollow portions of the side plates 32, 33 through the gaps on both sides of the rotor body 30. After the needle roller bearing 32a and the ball bearing 33a have been lubricated, they are returned to the oil tank T through the return holes 47 and 48.

The hydraulic pressure in each pump chamber 40 is mainly generated against the flow resistance in the gaps on both sides of the throttle hole 39 and the rotor body 30, and the magnitude of the flow resistance depends on the amount of oil flowing therethrough. The amount of oil corresponds to the magnitude of the relative rotation speed between the rotor and the casing. Therefore,
The level of the generated hydraulic pressure inside the pump chamber 40 corresponds to the difference in rotational speed between the input shaft 1 and the output shaft 2, in other words, the difference in rotational speed between the front and rear wheels. The driving force according to the speed difference is distributed from the front two wheels to the rear two wheels,
The four-wheel drive state is realized.

The drive coupling device including the vane pump 3 operates as described above, and the transmission characteristic of the driving force of the vane pump 3 depends on the hydraulic pressure generation characteristic of the vane pump 3. Therefore, each of the drive coupling devices can be operated in accordance with the relative rotation between the rotor and the casing. Reliable generation of hydraulic pressure in the pump chamber 40 is required. The oil pressure generation behavior inside the pump chamber 40 is as described above. To realize reliable oil pressure generation, the vanes 30a, 30a ...
It is important to reliably press against the inner peripheral surface of the and to realize high sealing performance between the adjacent vanes 30a, 30a. As described above, the pressing force of the vane 30a is the urging force of the coil springs 30c, 30c interposed between the vane 30a and the bottom of the storage groove 30b, and the hydraulic pressure introduced into the storage groove 30b through the discharge hole 44. Is. However, the latter has a pump chamber 4 at the tip of the vane 30a.
Since it cancels out with the hydraulic pressure acting inside 0, the quality of the sealing performance mainly depends on the former, that is, the quality of the biased state by the coil springs 30c and 30c. Therefore, whether or not the coil springs 30c, 30c ... Are properly mounted and the vanes 30a, 30a ... Can be pressed reliably without hindering their expansion and contraction is an important issue. The vane pump 3 according to the present invention solves this problem and, in order to reduce the labor required for mounting the coil springs 30c, 30c ..., The spring holder 5 for holding the coil springs 30c, 30c at the bottom of the storage groove 30b. Is equipped with.

FIG. 3 is a side view of the spring holder 5 which is a feature of the present invention, and FIG. 4 is an enlarged sectional view of an essential part showing a mounted state of the coil spring 30c.

The spring holder 5 includes a support plate 50 for supporting the spring holder 5 on the bottom of the storage groove 30b, and a pair of holding rods 51, 51 for holding the coil springs 30c, 30c separately. Support plate 50
Is a thin and thin plate material, both longitudinal ends of which are bent on the same side in the thickness direction as shown in the drawing, and the holding portions 50a, 50 for holding the rotor body 30 as described later.
a is formed. The tip ends of the holding portions 50a, 50a are slightly bent in the direction opposite to the bending direction so as to perform a guiding action during the holding. Further, the support plate 50 is formed with a pair of through holes 50b, 50b which are distributed from the center position in the longitudinal direction of the support plate 50 to both sides and penetrate the support plate 50 in the thickness direction. On the other hand, the holding rod 51 is a round rod formed by shaping one end into a hemispherical shape, and on the other side of the holding rod 51, a reduced diameter portion that reduces in diameter toward the end and an end portion of the reduced diameter portion. And a small-diameter portion that is continuous with.

The spring holder 5 has a through hole 50 as shown in the left half of FIG.
The small-diameter portions of the holding rods 51, 51 are inserted into the b, 50b from the surface of the support plate 50 (the surface opposite to the projecting sides of the holding parts 50a, 50a), and the projecting ends of the supporting plates 50, 50b. As shown in the right half of FIG. 3, the supporting plate 50 and the holding rods 51, 51 are integrated by caulking from the rear side of the former in a manner in which the latter is erected at a substantially right angle on the former. It is configured by converting. The coil springs 30c, 30c to be held by this are formed so that the seat portion on one side in the axial direction has a diameter slightly smaller than that of the other portion, as shown in the figure. By inserting the seat portion into the reduced diameter portion of the holding rod 51, it is securely held by the holding rod 51, and the coil springs 30c, 30c are retained by the holding rod 51 after the insertion. There is no danger of falling out of Further, since the holding rod 51 is a round rod and the tip portion is formed in a hemispherical shape, the coil spring
The fitting of 30c can be easily performed. Also, the coil spring 30c
The seats at both ends have two or more turns as shown.
As a result, when one is taken out of many coil springs 30c, 30c ... When being attached to the holding rod 51, the unnecessary coil spring 30c will not be taken out by being entangled with this.
It is possible to reduce the time required to mount the coil springs 30c, 30c.

The spring holding body 5 includes coil springs 30c, 3 for holding rods 51, 51, respectively.
With 0c held, as shown in Fig. 4, the rotor body
It is attached to the bottom of the storage groove 30b of 30. This mounting is performed by inserting the support plate 50 into the storage groove 30b from the side, and holding the bottom surfaces of the annular grooves 46, 46 on both sides of the rotor body 30 by the holding portions 50a, 50a on both sides of the support plate 50. , Storage groove 30b
Fixed to the bottom of the. As a result, the holding rods 51, 51 and the coil springs 30c, 30c attached to the holding rods 51, 51,
Is fixed radially outward along. The spring holder 5 is made of a material having excellent elasticity such as spring steel, and the holding parts 50a, 50a have sufficient elasticity. Therefore, the spring holding body 5 is inserted into the storage groove 30b as described above, the holding portions 50a, 50a ... After the tips are brought into contact with the bottom portion of the storage groove 30b, the holding portions 50a, 50a are lightly pushed in to hold the holding portion 50.
The a and 50a expand, and the rotor body 30 can be reliably held by these. In this way, the spring holder 5
Can be fixed easily and securely and then the vane 30
The rotor assembly is completed simply by inserting the vanes 30a into the storage grooves 30b while engaging the two notches 30d and 30d formed in the base portion of a with the tips of the coil springs 30c and 30c, respectively. Therefore, the rotor can be reliably assembled, and the number of assembling steps is significantly reduced.

Further, since the holding rods 51, 51 are round rods and have a circular cross section, when the coil springs 30c, 30c expand and contract, there is no fear of being obstructed by the holding rods 51, 51, and the vane 30a. Will be surely pressed.

The fixing method of the spring holding body 5 is not limited to that shown in this embodiment, and the holding portion 50 is inserted after the spring holding body 5 is inserted into the storage groove 30b.
Other fixing means, such as screwing a and 50a to the bottom surfaces of the annular grooves 46 and 46, respectively, may be used, but the one shown in this embodiment is
After the insertion, there is an advantage that the fixed state can be easily obtained by lightly pressing the spring holder 5.

Further, the holding rods 51, 51 for holding the coil springs 30c, 30c are not limited to those having the circular cross section shown in the present embodiment, and may have other cross sectional shapes such as an elliptical shape and a polygonal shape. .

Further, although the vane pump used in the drive connecting device for the four-wheel drive vehicle has been described in the present embodiment, it goes without saying that the application of the present invention is not limited to this.

〔effect〕

As described above in detail, in the case of the present invention, since the spring holding member is provided with the holding rod for externally fitting the coil spring, there is no deformation with time like the conventional fitting portion 61, and the movement of the vane can be performed. Will not be hindered.

Further, since the small-diameter seat portion of the coil spring is fitted to the reduced-diameter portion of the holding rod, this fitting work can be performed easily and surely.
The coil spring does not fall off the holding rod during assembly. Further, the expansion and contraction of the coil spring is repeated during pump operation, and the coil spring does not drop even if it is used in a vibrating device such as a drive connecting device.

Further, since the spring holding member is fixed across the annular groove provided for fluid flow, the locking hole 30e is formed in the rotor body.
There is no need to perform special processing such as forming a spring, and fixing of the spring holding member is simple. Further, the present invention can be applied regardless of whether the vane number is odd or even.

[Brief description of drawings]

FIG. 1 shows a configuration of the vane pump according to the present invention 4
FIG. 2 is a longitudinal sectional view of a drive coupling device for a wheel drive vehicle, FIG. 2 is an enlarged transverse sectional view taken along line II-II of FIG. 1, and FIG. 3 is a side view of a spring holder which is a feature of the present invention. FIG. 5 is a view showing a mounted state of a vane biasing coil spring in a vane pump according to the present invention, FIG. 5 is an enlarged view of a main part of a conventional vane pump, and FIG.
FIG. 7 and FIG. 7 are views showing a mounted state of a vane urging coil spring in a conventional vane pump. 3 ... Vane pump, 5 ... Spring holder, 30 ... Rotor body,
30a ... Vane, 30b ... Storage groove, 30c ... Coil spring, 31 ... Cam ring, 32, 33 ... Side plate, 50 ... Support plate, 51 ...
Holding rod

Front page continuation (72) Yoshihiro Nakagawa, Yoshihiro Nakagawa, Minami-ku, Osaka City, Osaka Prefecture Koyo Seiko Co., Ltd. (72) Yuji Ogawa, Togo Town, Aichi-gun, Aichi Prefecture In-house (72) Inventor Nakano Mitoku, Tochi-cho, Aichi-gun, Aichi-gun, Haruki, No. 1, Yakuike, Togo Seisakusho Co., Ltd. (56) Bibliography 62-105386 (JP, U) Actual public Sho-50-30650 (JP) , Y1) Suguko 31-16484 (JP, Y1)

Claims (1)

[Scope of utility model registration request] 1. A vane slidably inserted along each of a plurality of storage grooves formed on the peripheral surface of a cylindrical body is interposed between each of the storage groove bottoms. In a vane pump provided with a rotor biased radially outward by a coil spring, a holding rod for externally fitting and holding the coil spring is erected on a part of the holding rod, and the bottoms of the respective storage grooves are mutually erected. A spring holding member fixed across the fluid-flowing annular grooves formed at both ends of the rotor in the axial direction in a manner of communicating with the holding rod, wherein the holding rod has a shaft at the bottom side shaft end of the storage groove. The coil spring has a reduced diameter portion that reduces in diameter toward the end side, and the coil spring has a small diameter seat portion having a smaller diameter than the other shaft end portion on one shaft end side, and the small diameter seat portion is fitted to the reduced diameter portion. A vane pump characterized by being worn.