JP2015140776A - vane pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane pump which reduces the number of components and reduces operation sound.SOLUTION: A vane pump 10 includes: a housing 20 in which a pump chamber 20A is formed; a rotor 30 where a left end part is disposed in the pump chamber 20A; a coupling 40 which is attached to a right end part of the rotor 30 and transmits power from a driving source to the rotor 30; and a vane 50 which is attached to the left end part of the rotor 30, integrally rotates with the rotor 30, and divides the pump chamber 20A into multiple operation spaces. Facing surfaces of the rotor 30 and the coupling 40 are attracted to each other by magnetic force.

Description

  The present invention relates to a technology of a vane pump that transmits power from a drive source to a rotor via a coupling to rotate the rotor, and rotates the vane by the rotation of the rotor.

  2. Description of the Related Art Conventionally, a vane pump that partitions a pump chamber into a plurality of working spaces by rotating the vane in the pump chamber is used for a vacuum pump for an automobile or the like.

The vane type vacuum pump disclosed in Patent Document 1 includes a housing composed of a body and a cover, a rotor rotatably supported by the housing, an Oldham coupling coupled to the rotor, and rotating as the rotor rotates. And vanes to be provided.
The vane type vacuum pump disclosed in Patent Document 1 connects a drive shaft to a camshaft or a crankshaft or the like, and connects the drive shaft and the rotor via an Oldham coupling. The Oldham coupling rotates while absorbing the misalignment between the rotor and the drive shaft by sliding and rotating along the radial direction of the drive shaft.

JP 2010-112332 A

The Oldham coupling disclosed in Patent Document 1 is sandwiched between the rotor and the drive shaft by fitting the unevenness formed on both sides so that the longitudinal direction is orthogonal to the unevenness of the rotor and the drive shaft. Thus, the structure does not fall off the rotor and the drive shaft.
In such a structure, for example, when the housing, the rotor, the vane, and the Oldham coupling are configured as one unit, and when the Oldham coupling is sandwiched between the rotor and the drive shaft by bringing the unit close to the drive shaft, The Oldham coupling may fall off the rotor.

As a means for preventing the Oldham coupling from falling off, for example, as shown in FIG. 6, a rectangular hole is formed in the Oldham coupling, and the protrusion formed on the rotor is inserted into the hole. At the same time, a means for attaching a retaining pin to the projecting portion is conceivable.
The Oldham coupling is sandwiched between the rotor and the drive shaft during the operation of the vane pump, and is prevented from falling off. Therefore, the retaining pin prevents the Oldham coupling from falling off only when the vane pump is attached or detached.

  In other words, the vane type vacuum pump disclosed in Patent Document 1 may require parts that are necessary only to prevent the Oldham coupling from dropping off during attachment and detachment.

The Oldham coupling is connected to the drive shaft in a state where a predetermined clearance is formed between the rotor and the drive shaft in order to ensure the function of absorbing the misalignment between the rotor and the drive shaft. (See the clearance shown in FIG. 6).
Therefore, the vane-type vacuum pump disclosed in Patent Document 1 may collide with the Oldham coupling and the rotor, the Oldham coupling and the retaining pin, or the Oldham coupling and the drive shaft during operation ( (See arrows shown in FIG. 6).

  The present invention has been made in view of the above situation, and provides a vane pump that can reduce the number of components and the operating noise.

  In Claim 1, the housing in which a pump chamber is formed inside, the rotor which one end part is arrange | positioned in the said pump chamber, and the other end part of the said rotor are attached, and the motive power from a drive source is transmitted to the said rotor. And a vane pump that is attached to one end of the rotor and rotates integrally with the rotor and divides the pump chamber into a plurality of working spaces, the rotor and the cup The opposite surface of the ring is attracted by magnetic force.

  According to a second aspect of the present invention, the opposing surfaces of the rotor and the coupling are attracted by a magnetic force by giving magnetism to the coupling.

  As effects of the present invention, the following effects can be obtained.

  According to the first aspect, the number of parts can be reduced and the operating noise can be reduced.

  In claim 2, the operating noise can be effectively reduced.

Explanatory drawing of a vane pump. Sectional drawing of a vane pump. The perspective view which shows a coupling. Sectional drawing which shows the state in which the coupling has adsorb | sucked to the rotor. Sectional drawing which shows the state in which the coupling is adsorb | sucking to the camshaft. Sectional drawing which shows the conventional Oldham coupling.

  Below, the vane pump 10 which concerns on this embodiment is demonstrated.

  In the following, for convenience of explanation, the vertical direction is defined based on the vertical direction of the paper surface in FIG. Further, the left and right direction is defined with reference to the left and right direction of the paper surface in FIG.

  The vane pump 10 is used as a negative pressure source of a brake booster (not shown), for example. The vane pump 10 according to the present embodiment is attached to, for example, an engine main body (a side surface of a cam carrier or the like).

  As shown in FIGS. 1 and 2, the vane pump 10 includes a housing 20, a rotor 30, a coupling 40, a vane 50, and a housing cover 60.

  The housing 20 is a substantially cylindrical member whose inner diameter and outer diameter decrease stepwise from the left end toward the right end.

  Note that the housing may be a substantially cylindrical member formed in a substantially elliptical shape when viewed from the axial direction.

  The side where the inner diameter of the housing 20 is large, that is, the left side is formed as a large diameter portion 21.

  The large diameter portion 21 is formed with a ring groove 21a on the left side surface. A seal member 21b is attached to the ring groove 21a. The large diameter portion 21 is provided with a suction passage 21c for sucking gas (air) from the brake booster to the pump chamber 20A. A check valve (not shown) for maintaining the negative pressure of the brake booster is provided in the suction passage 21c.

  Such a space inside the large-diameter portion 21 is formed as a pump chamber 20 </ b> A formed inside the housing 20.

The side where the inner diameter of the housing 20 is small, that is, the right side of the housing 20 is formed as a small diameter portion 22.
The housing 20 rotatably supports the rotor 30 by the inner peripheral surface of the small diameter portion 22.
In the small diameter portion 22, a ring groove 22a is formed on the outer peripheral surface. A seal member 22b is attached to the ring groove 22a. A through-hole penetrating along the left-right direction from the pump chamber 20A to the right side surface is formed below the small-diameter portion 22. The through hole is formed as a discharge passage 22 c for discharging gas from the pump chamber 20 </ b> A to the outside of the housing 20. A check valve 22d that opens and closes the discharge passage 22c is provided in the discharge passage 22c.

  The rotor 30 is arranged with its axis eccentric with respect to the axis of the pump chamber 20A. The rotor 30 has a left end (one end) disposed in the pump chamber 20A. The rotor 30 is formed with guide grooves 31 and protrusions 32.

  The guide groove 31 is a groove extending along the radial direction of the rotor 30, and is formed on the left side surface of the rotor 30.

  The protruding portion 32 is a portion that extends along the axial direction of the rotor 30 from the right side surface 33 of the rotor 30. The protrusion 32 is formed in a substantially rectangular shape when the rotor 30 is viewed from the axial direction.

  Such a rotor 30 is formed using a metal (for example, iron or the like) as a material.

  The rotor 30 is provided with a lubrication path for supplying lubricating oil to the pump chamber 20A. However, since it is not directly related to the present invention, the illustration is shown in FIG. 2, FIG. 4, and FIG. Omitted.

  As shown in FIGS. 2 and 3, the coupling 40 transmits power to the rotor 30. The coupling 40 is disposed on the right side of the rotor 30. The coupling 40 is formed with a hole 41 and a pair of protrusions 42.

The hole 41 is a hole that penetrates the coupling 40 in the axial direction (left-right direction in FIG. 2). The hole 41 is formed in a substantially rectangular shape when the coupling 40 is viewed from the axial direction. In FIG. 2, the longitudinal direction of the hole 41 is the depth direction of the drawing.
The protrusion 32 of the rotor 30 is inserted into the hole 41. The coupling 40 is supported so as to be movable relative to the rotor 30 in the axial direction and the longitudinal direction of the hole 41.
Thus, the coupling 40 is attached to the right end (other end) of the rotor 30.

The left side surface 43 of the coupling 40 faces the right side surface 33 of the rotor 30 (the surface of the right side surface of the rotor 30 on which the protruding portion 32 is not formed).
That is, in the vane pump 10 according to the present embodiment, the right side surface 33 of the rotor 30 and the left side surface 43 of the coupling 40 are opposed surfaces of the rotor 30 and the coupling 40.

  The pair of projecting portions 42 are portions extending along the right direction from the right side surface of the coupling 40. A pair of protrusion part 42 is formed in a substantially rectangular parallelepiped shape. The pair of projecting portions 42 are disposed to face each other with the hole 41 interposed therebetween.

  The pair of protrusions 42 are fitted into grooves 101 formed in the metal camshaft 100. The groove 101 of the camshaft 100 is a groove extending along a direction (vertical direction in FIG. 2) orthogonal to the longitudinal direction of the hole 41 of the coupling 40.

The coupling 40 is in a state in which a predetermined interval is left and right (axial direction) with respect to the rotor 30 and the camshaft 100, that is, in a state in which the coupling 40 cannot be in close contact with the rotor 30 and the camshaft 100 simultaneously. 100.
The coupling 40 has a structure that is sandwiched between the rotor 30 and the camshaft 100 and does not fall off.

  The coupling 40 rotates as the camshaft 100 rotates. At this time, the coupling 40 rotates while absorbing the misalignment between the rotor 30 and the camshaft 100 by sliding along the longitudinal direction of the protruding portion 32 of the rotor 30 and the groove 101 of the camshaft 100.

  As a result, the coupling 40 transmits power from the camshaft 100 that is a drive source to the rotor 30.

  That is, the coupling 40 according to the present embodiment is an Oldham coupling having an Oldham function (a function of absorbing misalignment of two axes).

  The coupling 40 according to the present embodiment is configured by a metal member having magnetism.

  The coupling 40 is configured as a member having magnetism, for example, by being given a strong impact during manufacturing or by being subjected to a heat treatment for imparting magnetism.

As shown in FIGS. 1 and 2, the vane 50 is a substantially plate-like member in which two concave portions extending along the longitudinal direction (vertical direction in FIGS. 1 and 2) are formed at both longitudinal ends. . The vane 50 is attached to the guide groove 31 of the rotor 30 (that is, one end portion of the rotor 30) so as to be slidable along the radial direction of the rotor 30, and is disposed in the pump chamber 20A. The vane 50 rotates integrally with the rotation of the rotor 30.
Caps 51 are attached to the front end portions (both ends in the longitudinal direction) of the vane 50.

Both caps 51 are fitted into recesses extending along the longitudinal direction of the vane 50. Both caps 51 slide while maintaining airtightness with the inner peripheral surface of the housing 20 as the vane 50 rotates in the direction of the arrow shown in FIG.
Thereby, the vane 50 partitions the pump chamber 20A as a plurality of working spaces that can be expanded and contracted.

  As shown in FIG. 2, the housing cover 60 is formed in a substantially disk shape. The housing cover 60 is disposed on the left side of the housing 20 and is attached to the left side surface of the housing 20 by a connecting member such as a bolt.

  Such a vane pump 10 is attached to an engine main body as follows, for example.

The vane pump 10 is configured as one unit by attaching the rotor 30 to the housing 20, attaching the coupling 40 and the vane 50 to the rotor 30, and then attaching the housing cover 60 to the housing 20.
At this time, the housing 20 and the housing cover 60 are sealed by the sealing member 21 b of the large diameter portion 21.

The vane pump 10 configured as one unit has a small diameter of the housing 20 in a hole formed in the engine body in a state where the phase of the pair of protrusions 42 of the coupling 40 is matched with the phase of the groove 101 of the camshaft 100. Part 22 is inserted. The coupling 40 is sandwiched between the rotor 30 and the camshaft 100 and is supported by the rotor 30 and the camshaft 100 so as not to drop off.
The vane pump 10 has a housing 20 fixed to the engine body with bolts or the like. The space between the housing 20 and the engine body is sealed by a seal member 22b of the small diameter portion 22.

Here, the coupling 40 is in a state movable relative to the rotor 30 in the left-right direction in order to secure the Oldham function.
Further, the rotor 30 according to the present embodiment is not provided with means for restricting the movement of the coupling 40 in the right direction (for example, a retaining pin as shown in FIG. 6).

  In this case, the coupling 40 moves to the right relative to the rotor 30 when the vane pump 10 is attached to the engine body or when the vane pump 10 is removed from the engine body, that is, when the vane pump 10 is attached or detached. There is a possibility of dropping off from the rotor 30.

  Therefore, the vane pump 10 according to the present embodiment employs a coupling 40 formed of a magnetic metal member as a coupling for connecting the rotor 30 and the camshaft 100.

According to this, as shown in FIG. 4, the vane pump 10 can adsorb the right side surface 33 of the rotor 30 and the left side surface 43 of the coupling 40 by magnetic force at the time of attachment / detachment (see the arrow shown in FIG. 4).
Therefore, the vane pump 10 can restrict the movement of the coupling 40 in the right direction with respect to the rotor 30 that is generated at the time of attachment / detachment by the magnetic force.

  For this reason, the vane pump 10 can reliably prevent the coupling 40 from dropping from the rotor 30 during attachment / detachment without providing the rotor 30 with means for restricting the movement of the coupling 40 in the right direction.

  Therefore, the vane pump 10 can reduce the retaining pins and the like necessary only to prevent the coupling 40 from dropping off when being attached or detached. That is, the vane pump 10 can reduce the number of parts.

  Moreover, the vane pump 10 can simplify the assembly process.

  Next, the operation of the vane pump 10 will be described.

As shown in FIGS. 1 and 2, the camshaft 100 rotates when the engine is driven. As the camshaft 100 rotates, the coupling 40 rotates integrally while absorbing the misalignment between the rotor 30 and the camshaft 100. The rotor 30 rotates when power from the camshaft 100 is transmitted through the coupling 40.
The vane 50 rotates while reciprocating the guide groove 31 of the rotor 30 by the rotation of the rotor 30.

As a result, the vane pump 10 changes the volume of the working chamber partitioned by the vane 50.
At this time, the vane pump 10 sucks the gas of the brake booster from the suction passage 21c and discharges the gas in the pump chamber 20A from the discharge passage 22c.

As described above, the coupling 40 is coupled to the rotor 30 and the camshaft 100 in a state where a predetermined interval is left and right with respect to the rotor 30 and the camshaft 100.
Therefore, the coupling 40 may move in the left-right direction when the vane pump 10 is operated, and may collide with the rotor 30 or the camshaft 100.

Therefore, as shown in FIG. 4, the vane pump 10 according to the present embodiment employs a coupling 40 having magnetism, and the right side surface 33 of the rotor 30 and the left side surface 43 of the coupling 40 are separated by magnetic force even during operation. Adsorption (see arrow shown in FIG. 4).
That is, the vane pump 10 can regulate the movement of the coupling 40 in the left-right direction with respect to the rotor 30 by the magnetic force even during operation.

Accordingly, the vane pump 10 can suppress the coupling 40 from moving in the left-right direction during operation and the coupling 40 from colliding with the rotor 30 or the camshaft 100.
That is, the vane pump 10 can reduce operating noise.

  As described above, the vane pump 10 adsorbs the right side surface 33 of the rotor 30 and the left side surface 43 of the coupling 40 (opposing surfaces of the rotor 30 and the coupling 40) by magnetic force.

  That is, the magnetic strength of the coupling 40 is strong enough to prevent the coupling 40 from falling off the rotor 30 due to the weight of the coupling 40 when the vane pump 10 is attached and detached, and the Oldham function is ensured when the vane pump 10 is operated. It is weak as much as possible.

Note that the vane pump may adsorb the rotor and the opposed surface of the coupling by a magnetic rotor and a non-magnetic coupling.
In this case, the rotor is configured as a member having magnetism, for example, by being subjected to a strong impact during manufacture or by being subjected to a heat treatment for imparting magnetism.

  In other words, the vane pump according to the present invention may be one in which at least one of the rotor 30 and the coupling 40 has magnetism.

Here, the vane pump 10 according to the present embodiment employs a coupling 40 having magnetism.
According to this, as shown in FIG. 5, the vane pump 10 can adsorb the coupling 40 not only to the rotor 30 but also to the camshaft 100 by magnetic force (see the arrow shown in FIG. 5).

  In this case, in the coupling 40, the pair of protrusions 42 are attracted to the side surface of the groove 101 of the camshaft 100.

According to this, the vane pump 10 can adsorb the coupling 40 to the rotor 30 or the camshaft 100 even when the adsorbed state of the rotor 30 and the coupling 40 is released due to vibration of the engine or the like during operation.
That is, the vane pump 10 can prevent the coupling 40 and the camshaft 100 from repeatedly colliding until the rotor 30 and the coupling 40 are adsorbed again.

  For this reason, the vane pump 10 can effectively reduce the operation noise.

  Further, the vane pump 10 can adsorb the coupling 40 to the camshaft 100 even when the adsorbed state of the rotor 30 and the coupling 40 is released when the vane pump 10 is removed from the engine body.

  That is, the vane pump 10 can maintain the state in which the coupling 40 is adsorbed to the camshaft 100 even when the coupling 40 is detached from the rotor 30 when being removed from the engine body. Therefore, the vane pump 10 can more reliably prevent the coupling 40 from falling off the engine body.

  In this way, the vane pump 10 causes the coupling 40 to have magnetism, thereby attracting the right side surface 33 of the rotor 30 and the left side surface 43 of the coupling 40 (opposite surfaces of the rotor 30 and the coupling 40) by magnetic force.

In the case where the rotor 30 and the coupling 40 are adsorbed, when the coupling 40 moves along a direction orthogonal to the left-right direction, the force (attraction) acting on the coupling 40 is adsorbed. Less than the force required to release the state.
That is, since the coupling 40 is not restricted by the magnetic force to move in order to absorb the misalignment, the misalignment can be absorbed while being adsorbed to the rotor 30.
The same applies to the case where the coupling 40 and the camshaft 100 are adsorbed by magnetic force.

  That is, the vane pump 10 can reduce the number of parts and reduce the operation noise while securing the Oldham function by adsorbing the rotor 30 and the coupling 40 or the coupling 40 and the camshaft 100 by magnetic force.

  The means for giving magnetism to the rotor or the coupling is not limited to this embodiment. For example, magnetism is embedded by embedding magnets on the opposing surfaces (attracting surfaces) of the rotor and the coupling. You may have it.

10 Vane pump 20 Housing 20A Pump chamber 30 Rotor 33 Right side (opposite side)
40 Coupling 43 Left side (opposite side)
50 Vane

Claims (2)

A housing in which a pump chamber is formed, a rotor having one end disposed in the pump chamber, a coupling attached to the other end of the rotor and transmitting power from a driving source to the rotor, A vane pump that is attached to one end of the rotor and rotates integrally with the rotor, and divides the pump chamber into a plurality of working spaces,
Adsorbing the opposing surfaces of the rotor and the coupling by magnetic force;
Vane pump. By giving magnetism to the coupling, the opposing surfaces of the rotor and the coupling are attracted by magnetic force,
The vane pump according to claim 1.

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