JP2009250033A - Water pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a water pump that can change a flow rate by performing torque transmission utilizing a magnetic force between a drive-side rotor body in a non-contact state and a driven-side rotor, which can reduce an air gap between the drive-side rotor and the driven-side rotor. <P>SOLUTION: A drive-side rotor 3 provided with a magnet 64 and a driven-side rotor 4 provided with a guide ring 8 are rotatably supported by a common rotating support shaft 21. Furthermore, an in-support shaft pressure passage 22 is formed in the rotating support shaft 21 as an introduction path of negative pressure for making a pump flow rate variable. By adjusting the negative pressure introduced into a negative-pressure chamber V via the in-support shaft pressure passage 22, an overlapping amount of the magnet 64 and the guide ring 8 is changed to adjust a pump discharge amount. Because the magnet 64 and the guide ring 8 rotate with the common axial center L as a center, an air gap between the magnet and the guide ring can be significantly reduced. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a water pump used for a water-cooled engine or the like. In particular, the present invention relates to an improvement in a variable flow rate water pump.

  Conventionally, as disclosed in, for example, Patent Document 1 below, a water-cooled engine has been provided with a water pump for circulating cooling water through a cooling system.

  Further, in recent years, as this type of water pump, a driving side rotating body including a water pump pulley that receives driving force of an engine as a driving source, and a driven side rotating body including a pump impeller disposed in a pump vortex chamber are provided. There has been proposed a variable flow rate (also referred to as variable capacity) water pump that is arranged independently and that transmits rotational force from the driving side rotating body to the driven side rotating body in a non-contact manner.

  Hereinafter, an example of the configuration of this type of water pump will be described with reference to FIG. The water pump shown in FIG. 7 includes the water pump pulley c, the drive side casing d, and the slider e as the drive side rotating body b. The water pump pulley c is wound with an accessory belt f and receives the driving force of the engine. The drive side casing d is rotatably supported by a water pump housing g via a bearing h, and is connected to the water pump pulley c so as to rotate together. The slider e is slidable in the direction along the axial center along the inner peripheral surface of the drive side casing d. Further, the slider e is integrally connected to the inner peripheral surface of the drive side casing d by spline fitting or the like so as to receive the rotational force of the water pump pulley c via the drive side casing d. Yes. Further, a permanent magnet i as a magnetic member is attached to the inner surface of the slider e.

  On the other hand, the driven rotor m includes the pump impeller n and a guide ring o as a derivative (magnetic member). The pump impeller n is disposed in a pump vortex chamber p1 formed in the timing chain case p, and is rotatably supported by a solid rotary support shaft p2 formed integrally with the timing chain case p via an underwater bearing. Has been. The guide ring o is attached to the boss part n1 of the pump impeller n so as to rotate integrally, and an aluminum ring member o2 is attached to the outer periphery of the iron core o1. Further, the drive side rotating body b and the driven side rotating body m are partitioned by a partition wall q.

  The permanent magnet i attached to the slider e of the driving side rotating body b and the guide ring o provided on the driven side rotating body m can be opposed to each other with a predetermined interval across the partition wall q. (See the upper half of FIG. 7).

  Thus, when the permanent magnet i rotates with the rotation of the driving side rotating body b, the magnetic field around the guide ring o changes, and the ring member o2 of the guide ring o is in a direction that prevents the change of the magnetic field. Inductive current is generated. Along with the generation of the induced current, torque is generated in the ring member o2 of the induction ring o. As a result, the driven rotor m rotates, and the water pump is driven by the rotation of the pump impeller n.

  Next, a configuration for making the pump flow rate variable will be described. In order to make the pump flow rate variable, the axial overlap amount (dimensions overlapping each other in the axial direction) between the permanent magnet i and the guide ring o can be changed. That is, by changing the overlap amount, the transmission torque to the driven-side rotator m is changed, whereby the water pump flow rate (pump discharge amount) can be changed.

  Specifically, the space between the drive side casing d and the slider e is configured as a negative pressure chamber r, and the coil spring s is accommodated in the negative pressure chamber r in a compressed state. By this coil spring s, an urging force is applied to the slider e so that the permanent magnet i is at a position facing the induction ring o. Further, a negative pressure introduction hole d1 is formed at the center of the drive side casing d, and a negative pressure pipe t is connected to the negative pressure introduction hole d1, so that a negative pressure chamber is provided via the negative pressure introduction hole d1. It enables the action of negative pressure on r. For example, the negative pressure pipe t is connected to an intake manifold of the engine, and a switching valve (not shown) is provided in the middle of the negative pressure pipe t. As a connection structure of the negative pressure pipe t, a bearing t1 and an air seal t2 are fitted into the negative pressure introduction hole d1 of the drive side casing d.

As an operation to change the pump flow rate, when the negative suction pressure of the engine is applied to the negative pressure chamber r by the switching operation of the switching valve, the sliding movement of the slider e against the urging force of the coil spring s causes the above-described sliding movement. The amount of overlap decreases, the torque generated in the ring member o2 decreases, and the pump flow rate decreases (see the lower half state in FIG. 7). On the other hand, if the switching valve is switched so that the negative suction pressure of the engine does not act on the negative pressure chamber r, the slider e slides due to the biasing force of the coil spring s, and the amount of overlap increases. The torque generated in the ring member o2 increases and the pump flow rate increases (see the upper half state in FIG. 7).
JP-A-9-88592

  However, the variable flow rate water pump configured as described above has the following problems.

  That is, in the variable flow rate water pump shown in FIG. 7, the driving side rotating body b is rotatably supported by the water pump housing g, while the driven side rotating body m is rotatably supported by the rotation support shaft p2. Yes. That is, the driving side rotating body b and the driven side rotating body m are rotatably supported by different members. For this reason, it is difficult to make the rotation axis of the driving side rotating body b coincide with the rotation axis of the driven side rotating body m (arranged on the same axis). In consideration of the deviation of the rotation axis, the interval between the permanent magnet i and the partition wall q and the induction ring o so that the permanent magnet i and the guide ring o do not come into contact with the partition wall q. It was necessary to set a large distance between the partition walls q. That is, it is necessary to set a large interval (hereinafter referred to as an air gap) between the permanent magnet i and the induction ring o.

  For this reason, even when the axial overlap amount between the permanent magnet i and the induction ring o is maximized, the air gap between the permanent magnet i and the induction ring o is large. Thus, it is difficult to ensure a large transmission torque from the driving side rotating body b to the driven side rotating body m, and the transmission efficiency of this torque cannot be sufficiently increased.

  Further, since the air gap needs to be set large, the permanent magnet i is increased in size, and as a result, it is difficult to reduce the size of the pump. For this reason, it is difficult to put it into practical use in terms of mountability on a vehicle, and the manufacturing cost of the pump itself is likely to increase.

  Further, in the configuration shown in FIG. 7, since it is necessary to connect the negative pressure pipe t that is a non-rotating member to the driving side casing d that is a rotating member, the driving side casing d and the negative pressure pipe t It is necessary to provide a bearing t1 and an air seal t2 between the two. For this reason, the number of parts increases, the manufacturing cost increases, and the assembling work is complicated.

  The present invention has been made in view of such a point, and the object of the present invention is to make the flow rate variable by transmitting torque between the driving side rotating body and the driven side rotating body in a non-contact state. An object of the present invention is to provide a water pump that can reduce the distance (air gap) between the driving side rotating body and the driven side rotating body.

-Solving principle-
The solution principle of the present invention taken in order to achieve the above object is that the driving side rotating body and the driven side rotating body are rotatably supported on the same rotation support shaft, so that these driving side rotating bodies Displacement between the rotation axis and the rotation axis of the driven-side rotator is eliminated, thereby enabling the air gap between the magnetic members provided on the drive-side rotator and the driven-side rotator to be set small. I have to.

-Solution-
Specifically, the present invention includes a driving side rotating body that rotates by transmitting a driving force from a driving source, and a driven side rotating body that has a pump impeller and is rotatably supported by a rotating support shaft, By changing the relative facing position of the driving side magnetic member provided on the driving side rotating body and the driven side magnetic member provided on the driven side rotating body, the driving side rotating body is changed to the driven side rotating body. Assuming a water pump configured to change the magnitude of the rotational force transmitted to. The water pump is provided with a pressure chamber in which the pressure generated by the pressure generation source can act as a driving force for changing the relative facing position of the driving side magnetic member and the driven side magnetic member. Further, the driving side rotating body and the driven side rotating body are rotatably supported by the common rotating support shaft. Here, the magnetic member means not only a member made of a material exhibiting ferromagnetism but also a member made of a material exhibiting paramagnetism. Further, the magnetic member includes a member in which a member made of a material exhibiting ferromagnetism and a member made of a material exhibiting paramagnetism are integrally combined.

  With this specific matter, one magnetic member moves (eg, slides) with respect to the other magnetic member by applying pressure (eg, negative pressure) generated by the pressure generation source to the pressure chamber. As a result, the relative opposing position of the driving side magnetic member and the driven side magnetic member (for example, the amount of overlap in the sliding movement direction) is changed, and the rotational force transmitted from the driving side rotating body to the driven side rotating body. Is changed, and the flow rate of the water pump is changed. And since the said drive side rotary body and the driven side rotary body are each rotatably supported by the common rotating support shaft, each magnetic member with which the driven side rotary body and the drive side rotary body are equipped, Both are configured to rotate about the axis of the rotation support shaft. That is, each magnetic member can rotate without causing a shift in the rotation axis, and a gap (air gap) between the two can be set to be extremely small. In the configuration so far, the driving side rotating body and the driven side rotating body have different support structures, so that there is a possibility that the rotational axis centers of the two are misaligned. The gap was designed to be large. On the other hand, according to the present invention, since the magnetic members can be supported on the same axis, the air gap can be greatly reduced, and the drive side rotary body to the driven side rotary body. The transmission loss of the transmitted torque can be significantly reduced, and the driving efficiency of the water pump can be significantly increased. Further, since the magnetic member can be reduced in size as the air gap is reduced, the pump as a whole can be reduced in size.

  Specific examples of the structure for introducing pressure into the pressure chamber include the following. First, the drive source is an internal combustion engine. The rotation support shaft is provided integrally with a case member (for example, a timing chain case) provided in the internal combustion engine, and a support shaft pressure passage is formed inside the rotation support shaft. The pressure passage is communicated with the pressure generation source and the pressure chamber.

  Thus, for example, if suction negative pressure of the internal combustion engine is introduced into the pressure passage in the support shaft formed inside the rotation support shaft, this negative pressure is transferred to the pressure chamber through the pressure support passage in the support shaft. Will be introduced. That is, it is possible to form a pressure introduction path that allows the pressure generation source and the pressure chamber to communicate with each other using a rotation support shaft that is provided integrally with the case member. In other words, it is possible to combine the function for supporting the driving side rotating body and the driven side rotating body on the same axis and the function for introducing the operating pressure into the pressure chamber. become. In addition, if a pipe for introducing pressure into the pressure chamber is connected to the pressure passage in the support shaft, this pipe can be connected to a non-rotating member. This eliminates the need for application, reduces the number of parts, and reduces the manufacturing cost and simplifies the assembly work.

  Specific configurations for rotatably supporting the driving side rotating body and the driven side rotating body by a common rotating support shaft include the following. In other words, the arrangement space for the driving-side rotator and the arrangement space for the driven-side rotator are partitioned by the partition walls. An opening for inserting the rotating support shaft is formed in the partition wall, and the drive side rotation is performed from the space where the driven rotating body is disposed between the edge of the opening and the outer peripheral surface of the rotating support shaft. The sealing material for preventing water leakage into the body arrangement space is provided.

  As described above, the rotation support shaft is inserted into the opening of the partition wall, so that the rotation support shaft can be arranged from the arrangement space of the driving side rotating body to the arrangement space of the driven side rotating body. Thus, the driving side rotating body and the driven side rotating body can be rotatably supported by a common rotating support shaft. In this case, there is a concern about water leakage from the opening of the partition wall, but water leakage is prevented by providing a sealing material between the edge of the opening of the partition wall and the outer peripheral surface of the rotation support shaft. .

  Specific examples of the configuration for changing the magnitude of the rotational force transmitted from the driving side rotating body to the driven side rotating body include the following. First, the drive-side rotator is provided with a water pump pulley that receives a driving force from a drive source, and a slider mechanism that is slidably accommodated inside the water pump pulley, and the pressure chamber includes: A space between the water pump pulley and the slider mechanism is formed. Further, the slider mechanism portion is made of an elastic material that supports the drive-side magnetic member and is slidable in a direction along the axis of the rotation support shaft, and an elastic material that connects the water pump pulley and the slider. Provide with a diaphragm. The diaphragm is elastically deformed according to the pressure acting on the pressure chamber and the slider slides to change the relative facing position of the driving side magnetic member and the driven side magnetic member. Yes.

  According to this configuration, when the pressure applied to the pressure chamber is released from the state in which the pressure is applied to the pressure chamber and the diaphragm is elastically deformed to change the relative facing position between the magnetic members, Due to the restoring force, the relative opposing positions of the magnetic members are quickly returned to the original positions. For example, when the pressure is applied to the pressure chamber and the discharge rate of the water pump is limited, the response to the pressure chamber is released and the response to the water pump is maximized. The discharge amount of the water pump according to the request can be secured quickly.

  Other configurations for changing the magnitude of the rotational force transmitted from the driving side rotating body to the driven side rotating body include the following. That is, the drive-side rotator is provided with a water pump pulley that receives a driving force from a drive source, and a slider mechanism that is slidably accommodated inside the water pump pulley, and the pressure chamber is A space between the water pump pulley and the slider mechanism is formed. Further, the slider mechanism section is provided with a slider that supports the drive side magnetic member and is slidable in a direction along the axis of the rotation support shaft. Furthermore, this slider is extrapolated to a high-density fiber body provided on the water pump pulley, and is supported so as to be slidable in the axial direction. The slider is slid according to the magnitude of the pressure acting on the pressure chamber to change the relative facing position between the driving side magnetic member and the driven side magnetic member.

  According to this configuration, it is possible to realize a configuration for moving the slider with a relatively simple configuration such as providing a high-density fiber body in the water pump pulley, and it is possible to reduce the number of parts and simplify the configuration.

  In the present invention, the drive-side rotator and the driven-side rotator are rotatably supported on the same rotation support shaft so that the rotation axis of the drive-side rotator and the rotation axis of the driven-side rotator are This eliminates misalignment, thereby making it possible to set a small air gap between the magnetic members provided on the driving side rotating body and the driven side rotating body. For this reason, transmission loss of torque transmitted from the driving side rotating body to the driven side rotating body can be significantly reduced, and the driving efficiency of the water pump can be significantly increased.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. This embodiment demonstrates the case where this invention is applied to the water pump for vehicles which is mounted in the engine for motor vehicles and operate | moves by receiving the driving force from an engine.

(First embodiment)
-Overall configuration of water pump-
FIG. 1 is a cross-sectional view of a water pump 1 according to this embodiment. As shown in FIG. 1, the water pump 1 does not include a water pump housing that constitutes a pump housing, and a rotation support shaft 21 described later is integrated with an engine timing chain case (case member) 2. The rotary pump 21 is attached to support substantially the entire water pump 1. The water pump 1 is disposed on the front surface of the engine (a surface on the vehicle front side in the case of a vertically mounted engine, a surface on the side of the vehicle in the case of a horizontally mounted engine). The rotating support shaft 21 is integrally attached to the timing chain case 2 by being fitted into and fixed to a recess 20 formed in the timing chain case 2.

  And this water pump 1 is arrange | positioned in the non-contact state with respect to this drive side rotary body 3 which rotates by receiving the drive force from an engine, and this drive side rotary body 3 is mentioned later. The configuration includes a driven side rotating body 4 that rotates by receiving a rotational force from the driving side rotating body 3. The feature of the present embodiment is that the driving side rotating body 3 and the driven side rotating body 4 are rotatably supported by the same rotating support shaft 21. Hereinafter, the configuration of the driving side rotating body 3 and the driven side rotating body 4 and the support structure thereof will be described in detail.

<Configuration of Driving Rotator 3>
First, the configuration of the drive side rotator 3 will be described. The drive-side rotator 3 includes a water pump pulley 5 and a slider mechanism unit 6.

  The water pump pulley 5 includes a substantially cylindrical pulley body 51 and a belt winding portion 53 that extends from the pulley body 51 to the outer peripheral side via a pulley sheet 52 and around which the auxiliary belt B is wound. .

  The pulley body 51 includes a disk-shaped disk part 55 and first to third cylinder parts 56, 57, 58. The disk portion 55 has an opening 55 a for inserting the rotation support shaft 21 at the center portion.

  The first cylindrical portion 56 is formed as a cylindrical member extending in the horizontal direction from the outer peripheral edge of the disc portion 55 toward the timing chain case 2 side (the right side in FIG. 1).

  The second cylinder portion 57 is formed as a cylindrical member extending in the horizontal direction from the inner peripheral edge of the disc portion 55 toward the timing chain case 2 side (right side in FIG. 1). The length dimension of the second cylinder part 57 in the axial direction (horizontal direction) is set shorter than the length dimension of the first cylinder part 56 in the axial direction. Further, the inner diameter dimension of the second cylindrical portion 57 is set slightly larger than the outer diameter dimension of the rotary support shaft 21.

  The third cylindrical portion 58 has a cylindrical shape that extends in the horizontal direction from the position slightly on the outer peripheral side of the inner peripheral edge of the disc portion 55 toward the side opposite to the timing chain case 2 side (the left side in FIG. 1). It is formed as a member.

  A ball bearing 54 is disposed between the inner peripheral surface of the third cylindrical portion 58 and the outer peripheral surface of the rotary support shaft 21 in the pulley main body 51. Thereby, the water pump pulley 5 is supported by the rotation support shaft 21 so as to be rotatable around the horizontal axis. That is, the rotation center of the water pump pulley 5 is the axis L of the rotation support shaft 21.

  In addition, the second cylindrical portion 57 is formed with an opening 57a penetrating in the radial direction at a position facing a later-described support shaft pressure passage 22 formed in the rotation support shaft 21. Further, air seals 23 and 24 are interposed at two locations between the inner peripheral surface of the second cylindrical portion 57 and the outer peripheral surface of the rotary support shaft 21. The air seals 23 and 24 are disposed on both sides in the axial direction with respect to the opening 57a formed in the second cylindrical portion 57. That is, the air seals 23 and 24 form a partitioned space S between the inner peripheral surface of the second cylindrical portion 57 and the outer peripheral surface of the rotary support shaft 21, and the opening 57 a and the support shaft internal pressure are formed. The passages 22 communicate with the partitioned spaces S, respectively.

  The accessory belt B is wound around the outer peripheral surface of the belt winding portion 53. This auxiliary machine belt B is stretched over pulleys provided in various auxiliary machines in addition to a crank pulley (not shown) attached to the crankshaft of the engine. For this reason, when the engine is driven, the rotational driving force of the crankshaft of the engine is transmitted to each auxiliary machine via the auxiliary machine belt B, and is also transmitted to the belt wrapping portion 53 for the water pump pulley 5. The water pump pulley 5 rotates around the horizontal axis.

  The slider mechanism 6 is accommodated in the pulley body 51 of the water pump pulley 5 and includes a slider 62 and a diaphragm 63.

  The slider 62 includes a cylindrical portion 62a that contacts the inner peripheral surface of the first cylindrical portion 56 of the pulley body 51, and an inner peripheral side from one end of the cylindrical portion (the end opposite to the timing chain case 2 side). And a disc portion 62b extending toward the end, and is slidably disposed in the direction along the axis L (the left-right direction in FIG. 1) along the inner peripheral surface of the first tube portion 56. The inner diameter dimension of the disc part 62 b is set larger than the outer diameter dimension of the second cylinder part 57.

  The slider 62 is fitted so as not to rotate relative to the first cylindrical portion 56. When the water pump pulley 5 rotates, the rotational force is transmitted to the slider 62 via the pulley body 51, and the slider 62 The entire mechanism unit 6 rotates integrally with the water pump pulley 5.

  In addition, an O-ring O1 is provided on the outer peripheral surface of the cylindrical portion 62a of the slider 62, and seals between the inner peripheral surface of the first cylindrical portion 56 in an airtight state. And the magnet (permanent magnet) 64 as a cylindrical drive side magnetic member which comprises a part of rotational force transmission structure is integrally attached to the internal peripheral surface of this cylinder part 62a.

  The diaphragm 63 is made of rubber, for example, and has a substantially circular shape that connects one end portion (end portion on the timing chain case 2 side) of the second cylindrical portion 57 and the inner peripheral edge of the disc portion 62b of the slider 62. It is formed of a plate-shaped member. Thereby, the space formed between the pulley main body 51 and the slider mechanism part 6 is formed as the negative pressure chamber V as a substantially sealed space cut off from the outside air.

  Further, the pressure passage 22 in the support shaft formed inside the rotation support shaft 21 opens to one end side of the rotation support shaft 21 (an end portion on the opposite side to the timing chain case 2 side). An axial passage 22a extending along the axis of the shaft 21 and a radial passage 22b extending from the other end of the axial passage 22a toward the outer side in the radial direction of the rotary support shaft 21 are provided. The opening end of the radial passage 22b faces the opening 57a of the second cylindrical portion 57 as described above. For this reason, the negative pressure chamber V communicates with the pressure passage 22 in the support shaft through the opening 57a formed in the second cylindrical portion 57 and the space S formed between the air seals 23 and 24. Yes.

  Further, the diaphragm 63 is elastically deformed, so that the slider 62 is allowed to slide (slide movement) along the inner peripheral surface of the first cylindrical portion 56 in the pulley body 51. FIG. 1 shows a state in which the slider 62 has moved to the position closest to the timing chain case 2, and FIG. 2 shows a state in which the slider 62 has moved to the maximum slide position on the side opposite to the timing chain case 2 side. ing. A stopper 56a is provided at the end of the inner surface of the first cylindrical portion 56 on the timing chain case 2 side so as to regulate the maximum slide position of the slider 62 toward the timing chain case 2 side. At this position, the overlap amount of the magnet 64 with respect to the guide ring 8 described later is maximized.

  As described above, the drive-side rotator 3 is rotatably supported by the rotation support shaft 21 that extends from the timing chain case 2 in the horizontal direction. That is, the magnet 64 provided in the drive-side rotator 3 is configured to rotate about the axis L of the rotation support shaft 21 as a rotation center.

<Configuration of driven-side rotating body 4>
Next, the configuration of the driven side rotating body 4 will be described. The driven side rotating body 4 includes a pump impeller 7 and a guide ring 8 as a driven side magnetic member.

  The pump impeller 7 is disposed in a pump vortex chamber 26 formed by a recessed portion 25 provided on the surface of the timing chain case 2, and is rotatably and axially supported by the rotary support shaft 21 through an underwater bearing or the like. The slide movement in the direction of the heart is supported in an impossible manner. Then, the cooling water in the pump vortex chamber 26 is sent out to the cooling water passage of the engine by the rotation of the pump impeller 7, whereby the cooling water is circulated.

  The induction ring 8 is attached to the boss portion 71 of the pump impeller 7 so as to be integrally rotated, and an aluminum ring member 82 is attached to the outer periphery of the iron core 81.

  The guide ring 8 is disposed at the position where the slider 62 is moved to the position closest to the timing chain case 2 (the state shown in FIG. 1). In a state where it is moved to the maximum slide position on the side opposite to the timing chain case 2 side (the state shown in FIG. 2), the entirety is set so as not to face the magnet 64.

  As described above, the driven-side rotating body 4 is rotatably supported by the rotating support shaft 21 extending in the horizontal direction from the timing chain case 2, similarly to the driving-side rotating body 3. That is, the guide ring 8 provided in the driven side rotating body 4 is configured to rotate about the axis L of the rotation support shaft 21 as the rotation center, similarly to the magnet 64.

<Configuration of partition wall>
The space in which the driving side rotator 3 is disposed and the space in which the driven side rotator 4 is disposed are partitioned by a partition wall 9. Specifically, the partition wall 9 is a substantially circular sheet metal member having an opening 91 formed in the center. In addition, the partition wall 9 includes an outer peripheral disc portion 92 located on the outer peripheral side, a cylindrical portion 93 continuous on the inner peripheral side of the outer peripheral disc portion 92, and an inner peripheral side from one end of the cylindrical portion 93. And an inner circumferential disc portion 94 that extends.

  The outer peripheral edge of the outer peripheral disk portion 92 is bolted to the timing chain case 2. Note that an O-ring (not shown) is interposed between the outer peripheral disk portion 92 and the timing chain case 2.

  The cylindrical portion 93 is disposed between the magnet 64 and the guide ring 8, and is disposed with a slight gap (air gap) between them. Thus, the magnet 64 and the guide ring 8 are arranged to face each other with the cylindrical portion 93 interposed therebetween when the slider 62 is in the slide position shown in FIG. Thus, when the engine is driven with the magnet 64 and the induction ring 8 facing each other, and the magnet 64 rotates with the rotation of the driving side rotating body 3, the magnetic field around the induction ring 8 changes, An induced current is generated in the ring member 82 of the induction ring 8 in a direction that prevents the change in the magnetic field. Along with the generation of the induction current, a torque is generated in the ring member 82 of the induction ring 8, and as a result, the driven side rotating body 4 rotates and the water pump 1 is driven by the rotation of the pump impeller 7. .

  The inner peripheral disc portion 94 includes the opening 91 at the center thereof, and the rotation support shaft 21 is inserted into the opening 91. An O-ring O2 is interposed between the edge of the opening 91 and the outer peripheral surface of the rotary spindle 21.

  In this way, the space (atmosphere side space) in which the drive side rotator 3 is disposed and the space (cooling water side space) in which the driven side rotator 4 is disposed are partitioned by the partition wall 9. ing.

-Configuration for negative pressure supply and negative pressure supply operation-
Next, a configuration for supplying a negative pressure to the negative pressure chamber V will be described.

  In order to make the pump flow rate variable, the axial overlap amount (dimension overlapping each other in the axial direction) between the magnet 64 and the guide ring 8 can be changed. In other words, by changing the overlap amount, the torque transmitted from the drive-side rotator 3 to the driven-side rotator 4 is changed, thereby changing the rotation speed of the driven-side rotator 4 and the water pump. The flow rate (pump discharge amount) can be changed.

  In this embodiment, the suction negative pressure generated in the intake manifold of the engine is used as a power source for changing the overlap amount. This will be specifically described below.

  First, as described above, at the central portion of the rotation support shaft 21, one end opens to one end side of the rotation support shaft 21 (end opposite to the timing chain case 2 side), and the other end enters the negative pressure chamber V. A pressure shaft 22 in the support shaft that communicates is formed.

  A negative pressure pipe 13 is connected to one end of the support shaft pressure passage 22 via a cylindrical socket 12. The negative pressure pipe 13 is connected to the engine via a VSV (vacuum switching valve) 14. It communicates with the intake manifold. The VSV 14 is a valve for switching a space in which the support shaft pressure passage 22 communicates, and in accordance with an output signal from the ECU 15, a switching state (hereinafter referred to as the support shaft pressure passage 22 communicates with the atmosphere). It is possible to switch between a first switching state and a switching state (hereinafter referred to as a second switching state) in which the pressure passage 22 in the support shaft communicates with the intake manifold.

  For this reason, if the suction negative pressure in the intake manifold is not applied to the negative pressure chamber V with the VSV 14 in the first switching state, the pressure in the space on both sides of the slider mechanism 6 is equalized, and the diaphragm 63 is elastic. Without being deformed, the slider 62 is moved to the position closest to the timing chain case 2, and substantially the entire magnet 64 faces the induction ring 8. That is, the amount of overlap in the axial direction between the two increases, the torque generated in the ring member 82 increases, and the pump flow rate becomes maximum.

  On the other hand, if the suction negative pressure in the intake manifold is applied to the negative pressure chamber V via the negative pressure pipe 13 and the support shaft pressure passage 22 with the VSV 14 in the second switching state, for example, as shown in FIG. As the diaphragm 63 is elastically deformed, the slider 62 slides and the amount of overlap between the magnet 64 and the guide ring 8 in the axial direction is small, or the amount of overlap is “0”, which occurs in the ring member 82. The torque to be reduced decreases and the pump flow rate decreases. In this case, as the negative pressure applied to the negative pressure chamber V increases, the axial overlap amount between the magnet 64 and the guide ring 8 decreases and the pump flow rate decreases. That is, it is possible to adjust the pump flow rate by adjusting the magnitude of the negative pressure (for example, by adjusting the switching operation (duty control operation) of the VSV 14).

  For example, when the engine is cold, such as when the engine is started, the negative pressure applied to the negative pressure chamber V is set large, the overlap amount is decreased, the pump flow rate of the water pump 1 is decreased, and the engine warms up early. Make a chance. Further, when the engine is warmed up, the negative pressure applied to the negative pressure chamber V is set small, the overlap amount is increased, the pump flow rate of the water pump 1 is increased, and the cooling efficiency is improved. It is possible to use in a manner such as

  When the negative pressure applied to the negative pressure chamber V is set large and the slider 62 is moved to the maximum slide position on the side opposite to the timing chain case 2 as shown in FIG. Since the magnetic field of the magnet 64 hardly acts on the induction ring 8 because of “0”, the induced current generated in the induction ring 8 becomes almost “0”. Thereby, the transmission torque to the driven side rotating body 4 becomes substantially “0”, and the water pump 1 stops.

-Effect of the embodiment-
As described above, in the present embodiment, both the driving side rotating body 3 and the driven side rotating body 4 are rotatably supported by the rotation support shaft 21. That is, the magnet 64 provided on the drive side rotating body 3 and the guide ring 8 provided on the driven side rotating body 4 are both configured to rotate about the axis L of the rotation support shaft 21 as a rotation center. It has become. For this reason, there is no deviation in the rotational axis between the magnet 64 and the guide ring 8, and the gap (air gap) between the two can be managed with high accuracy. In the configuration of the water pump shown in FIG. 7, since the driving side rotating body b and the driven side rotating body m have different support structures, the magnet i or the induction is used when the rotational axis centers of the both are shifted. In consideration of the possibility that the ring o comes into contact with the partition wall q, it is necessary to design the air gap to be large (for example, about 1 mm). On the other hand, in the configuration of the present embodiment, this air gap can be significantly reduced (for example, designed to be about 0.3 mm). For this reason, the transmission loss of the torque transmitted from the drive side rotator 3 to the driven side rotator 4 can be greatly reduced, and the drive efficiency of the water pump 1 can be significantly increased. In addition, with this significant improvement in drive efficiency, even a water pump that is smaller than the conventional water pump can exhibit the same high performance as the conventional one.

  Further, the outer diameter of the magnet 64 can be reduced along with the reduction of the air gap described above, and this can also reduce the size of the water pump 1 as a whole.

  Further, in the configuration of the water pump shown in FIG. 7, the negative pressure pipe t needs to be connected to the drive-side casing d that is a rotating member. Therefore, the bearing t1 and the air seal t2 are required as this connection structure. According to the configuration of the present embodiment, since the negative pressure pipe 13 is connected to the rotation support shaft 21 that is a non-rotating member, it is not necessary to apply a bearing or an air seal to this connection location, and the number of parts is reduced. Thus, the manufacturing cost can be reduced and the assembling work can be simplified.

(Second Embodiment)
Next, a second embodiment will be described. The water pump 1 according to the present embodiment is different from that of the first embodiment in the configuration of the slider mechanism section 6. Other configurations are substantially the same as those in the first embodiment. Accordingly, only differences from the first embodiment will be described here.

  3 and 4 are cross-sectional views of the water pump 1 according to the present embodiment, corresponding to FIGS. 1 and 2 in the first embodiment. 3 and 4, the same components as those of the first embodiment, which are the main components of the water pump 1, are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in these drawings, the slider mechanism 6 in the water pump 1 according to the present embodiment does not include the diaphragm 63, and the slider mechanism 6 is axially centered with respect to the second cylinder 57 of the pulley body 51. The high-density fiber body 65 is fixed to the outer peripheral surface of the second cylindrical portion 57, and the inner peripheral side edge of the disc portion 62b of the slider 62 is configured to be slidable in the direction along However, it is arrange | positioned so that the outer peripheral part of this high-density fiber body 65 may be contact | abutted. The high-density fiber body 65 is bundled with chemical fibers at a high density, and is fixed to the outer peripheral surface of the second cylindrical portion 57 by a technique such as winding or flocking over the entire sliding movement range of the slider mechanism portion 6. It is a thing. Thus, the fibers are bundled at a high density, so that the spaces on both sides of the slider mechanism portion 6, that is, the negative pressure chamber V and the atmosphere side are isolated in an airtight state.

  Therefore, if the suction negative pressure in the intake manifold is not applied to the negative pressure chamber V with the VSV 14 in the first switching state, the suction between the magnet 64 and the induction ring 8 is performed as shown in FIG. Due to the force, substantially the entire magnet 64 faces the induction ring 8. That is, the amount of overlap in the axial direction between the two increases, the torque generated in the ring member 82 increases, and the pump flow rate becomes maximum. On the other hand, when the suction negative pressure in the intake manifold is applied to the negative pressure chamber V with the VSV 14 in the second switching state, the amount of overlap between the magnet 64 and the guide ring 8 in the axial direction is as shown in FIG. Less or the overlap amount becomes “0”, the torque generated in the ring member 82 is reduced, and the pump flow rate is reduced.

  In addition, on the inner surface of the pulley main body 51 in the present embodiment, as shown in FIG. 4, a stopper 51a for regulating the position in a state where the slider 62 has moved to the maximum slide position on the side opposite to the timing chain case 2 side. Is provided. This stopper 51a is for preventing the opening 57a formed in the said 2nd cylinder part 57 from being closed by restrict | limiting the moving position of the slider 62. FIG.

  According to the configuration of the present embodiment, the following effects can be obtained in addition to the effects obtained by the configuration of the first embodiment described above. That is, by providing the slider mechanism 6 with the high-density fiber body 65, the number of parts can be reduced and the configuration can be simplified.

(Third embodiment)
Next, a third embodiment will be described. The water pump 1 according to this embodiment is also different from that of the first embodiment in the configuration of the slider mechanism section 6. Other configurations are substantially the same as those in the first embodiment. Therefore, only differences from the first embodiment will be described here.

  5 and 6 are cross-sectional views of the water pump 1 according to the present embodiment, corresponding to FIGS. 1 and 2 in the first embodiment. 5 and 6, the same components as those in the first embodiment, which are the main components of the water pump 1, are denoted by the same reference numerals, and the description thereof is omitted.

  As shown in these drawings, the slider mechanism portion 6 in the water pump 1 according to the present embodiment does not include the diaphragm 63 as in the second embodiment. As a difference from the second embodiment, the slider mechanism portion 6 is configured such that the inner peripheral side edge of the disc portion 62b of the slider 62 abuts on the outer peripheral surface of the second cylindrical portion 57, and this disc portion. An O-ring O3 is provided at the inner peripheral side edge of 62b, thereby ensuring the airtightness of the negative pressure chamber V.

  In addition, as shown in FIG. 6, the position in the state which the slider 62 moved to the largest slide position on the opposite side to the timing chain case 2 side is regulated on the outer peripheral surface of the said 2nd cylinder part 57 in this embodiment. A stopper 51b is provided. The stopper 51b is for restricting the moving position of the slider 62 so that the opening 57a formed in the second cylindrical portion 57 is not closed.

  In addition, since the adjustment operation | movement of the pump discharge amount in this embodiment is the same as that of each embodiment mentioned above, description here is abbreviate | omitted.

-Other embodiments-
Each embodiment described above demonstrated the case where this invention was applied to the vehicle water pump 1 which is mounted in the engine for motor vehicles and act | operates by receiving the driving force from an engine. The present invention is not limited to this, and can also be applied to a water pump used for applications other than those for automobiles. Further, the driving source of the water pump 1 is not limited to the internal combustion engine, and may be one that receives driving force from an electric motor (electric motor).

  Further, the suction negative pressure in the intake manifold is used as the negative pressure that is the driving force for sliding the slider 62. However, the present invention is not limited to this, and other negative pressure such as a vacuum pump is used. You may make it employ | adopt a generation source. Further, a positive pressure (pressurization) may be used as a driving force for sliding the slider 62.

  Further, in each of the above embodiments, the induction ring 8 is disposed on the inner circumferential side and the magnet 64 is disposed on the outer circumferential side, and the transmission torque to the driven side rotating body 4 is changed by sliding the magnet 64. . The present invention is not limited to this, and a configuration may be adopted in which a guide ring is disposed on the outer peripheral side and a magnet is disposed on the inner peripheral side, and the transmission torque to the driven rotor is changed by sliding the guide ring. Good.

  Further, in each of the above embodiments, the coil spring is used as the source of the urging force for returning the slider 62 to the original position when the negative pressure action on the negative pressure chamber V is released. It may be accommodated in a compressed state inside.

  Further, in each of the above embodiments, the pump vortex chamber 26 is formed by the recessed portion 25 provided on the surface of the timing chain case 2, but the pump vortex chamber is formed using a cylinder block. The present invention is also applicable to this case.

  Further, in each of the above embodiments, the support shaft pressure passage 22 formed in the rotation support shaft 21 is opened at one end side of the rotation support shaft 21 (the end opposite to the timing chain case 2 side). The negative pressure pipe 13 is connected to the open end. The present invention is not limited to this, and the pressure passage 22 in the support shaft is opened at the end on the timing chain case 2 side, and the negative pressure in the case communicated with the pressure passage 22 in the support shaft inside the timing chain case 2. It is good also as a structure which forms a channel | path, opens this negative pressure channel | path in a case at the end surface of the timing chain case 2, and connects negative pressure piping to this opening end. According to this, it is not necessary to secure a space for disposing the negative pressure introducing pipe on the front side of the water pump (outside of the side where the driving side rotating body is disposed). As a result, it is possible to save the space in the engine room. For example, it is possible to realize a water pump that can be mounted on a small vehicle having a relatively small engine room volume.

  Further, the rotation support shaft 21 may be integrally formed with the timing chain case 2.

It is sectional drawing which shows the state which is not making the negative pressure act in the water pump which concerns on 1st Embodiment. It is sectional drawing which shows the state which made the negative pressure act in the water pump which concerns on 1st Embodiment. It is sectional drawing which shows the state which is not making the negative pressure act in the water pump which concerns on 2nd Embodiment. It is sectional drawing which shows the state which made the negative pressure act in the water pump which concerns on 2nd Embodiment. It is sectional drawing which shows the state which is not making the negative pressure act in the water pump which concerns on 3rd Embodiment. It is sectional drawing which shows the state which made the negative pressure act in the water pump which concerns on 3rd Embodiment. It is sectional drawing of the water pump which concerns on a prior art example.

Explanation of symbols

1 Water pump 2 Timing chain case (case member)
DESCRIPTION OF SYMBOLS 21 Rotation spindle 22 Pressure channel 65 in a spindle High density fiber body 3 Drive side rotary body 4 Driven side rotary body 5 Water pump pulley 6 Slider mechanism part 62 Slider 63 Diaphragm 64 Magnet (drive side magnetic member)
7 Pump impeller 8 Guide ring (driven-side magnetic member)
9 Bulkhead 91 Opening V Negative pressure chamber (pressure chamber)
L Axis O2 O-ring (seal material)

Claims (5)

A driving-side rotating body that rotates by receiving a driving force transmitted from a driving source; and a driven-side rotating body that has a pump impeller and is rotatably supported by a rotation support shaft. The magnitude of the rotational force transmitted from the driving side rotating body to the driven side rotating body is changed by changing the relative facing position between the driving side magnetic member and the driven side magnetic member provided on the driven side rotating body. In a water pump configured to change
There is provided a pressure chamber in which the pressure generated by the pressure generating source can act as a driving force for changing the relative facing position between the driving side magnetic member and the driven side magnetic member,
The water pump, wherein the driving side rotating body and the driven side rotating body are rotatably supported by the common rotating support shaft. In the water pump according to claim 1,
The drive source is an internal combustion engine,
The rotating support shaft is provided integrally with a case member provided in the internal combustion engine, and a support shaft pressure passage is formed therein, and the support shaft pressure passage is connected to the pressure generating source and the pressure generating source. A water pump characterized by communicating with each pressure chamber. In the water pump according to claim 1 or 2,
The arrangement space of the driving side rotator and the arrangement space of the driven side rotator are partitioned by a partition wall,
The partition is formed with an opening through which the rotating support shaft is inserted, and is driven from the space where the driven rotating body is disposed between the edge of the opening and the outer peripheral surface of the rotating support shaft. A water pump, characterized in that a sealing material is provided for preventing water leakage into the space where the side rotor is disposed. In the water pump according to claim 1, 2, or 3,
The drive-side rotator includes a water pump pulley that receives a driving force from a drive source, and a slider mechanism that is slidably accommodated inside the water pump pulley. It is formed as a space between the water pump pulley and the slider mechanism,
The slider mechanism includes a slider that supports the drive-side magnetic member and is slidable in a direction along the axis of the rotation support shaft, and a diaphragm made of an elastic material that connects the water pump pulley and the slider; With
The diaphragm is elastically deformed according to the pressure acting on the pressure chamber, and the slider slides to change the relative facing position of the driving side magnetic member and the driven side magnetic member. A water pump characterized by In the water pump according to claim 1, 2, or 3,
The drive-side rotator includes a water pump pulley that receives a driving force from a drive source, and a slider mechanism that is slidably accommodated inside the water pump pulley. It is formed as a space between the water pump pulley and the slider mechanism,
The slider mechanism portion includes a slider that supports the drive-side magnetic member and is slidable in a direction along the axis of the rotation support shaft. The slider is mounted on a high-density fiber body provided on the water pump pulley. It is extrapolated and supported so that it can slide in the axial direction.
The slider is slid according to the pressure acting on the pressure chamber to change the relative facing position of the driving side magnetic member and the driven side magnetic member. Water pump.

Images