JP2019158043A - Flow rate adjustment device - Google Patents

Abstract

To provide a flow rate adjustment device capable of reducing the number of components of an amount adjustment valve.SOLUTION: A flow rate adjustment device comprises: a water pump 2 configured to pump cooling water; a pump housing 14 through which cooling water passes and which has a storage chamber 13; a valve body 33 disposed in the storage chamber 13 to adjust a pumping amount of cooling water with an impeller 15 by moving forward and backward from the storage chamber 13; a coil spring 34 disposed in the storage chamber 13 and configured to energize the valve body 33 so as to protrude from the storage chamber 13; and a thermal expansion body 35 disposed in the storage chamber 13 and configured to energize the valve body 33 so as to be stored in the storage chamber 13. The thermal expansion body 35 increases the energization force as the temperature of the cooling water increases, and stores the valve body 33 in the storage chamber 13 against the energization force of the coil spring 34.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a flow rate adjusting device.

Conventionally, as an example of a flow rate adjusting device, a water pump that pumps fluid, a fluid path through which the fluid flows, and a fluid path that adjusts the flow rate of the pumped fluid by increasing and decreasing the temperature of the cooling water There is known a device including a flow rate adjusting device. (Patent Document 1)
In such a flow rate adjusting device, a gate type is used in which the valve body is advanced and retracted by the driving force of the motor to adjust the fluid pumping amount.

JP 2017-67016 A

  However, in the flow rate adjusting device of Patent Document 1, a motor is used as a drive source for moving the valve body back and forth. Generally, a motor is composed of many parts such as a rotor and a stator, and a mechanism for converting the rotational force of the motor into the advancing and retracting direction of the valve body is also required. For this reason, the flow rate adjusting device using a motor as a drive source may increase the number of parts.

  This invention is made | formed in view of such a situation, The objective is to provide the flow volume adjusting device which reduces the number of parts of a flow volume adjusting device.

  A pump that solves the above-described problems is a pump that pumps fluid, a housing that passes the fluid and that has a storage chamber, and is disposed in the storage chamber, and advances and retreats from the storage chamber so that the fluid by the pump A valve body that adjusts the pumping amount of the gas, a first biasing member that is disposed in the storage chamber and biases the valve body so as to protrude from the storage chamber, and is disposed in the storage chamber. A second urging member for urging the body to be stored in the storage chamber, and the urging force of the second urging member increases as the temperature rises, and the urging force of the first urging member is increased. The valve body is stored in the storage chamber against the force.

  According to the above configuration, when the fluid is pumped from the pump, the valve body moves forward and backward from the storage chamber to adjust the fluid pumping amount. The valve body protrudes from the storage chamber by the biasing force of the first biasing member, and is stored in the storage chamber by the biasing force of the second biasing member. Note that the urging force of the second urging member increases or decreases as the temperature of the fluid rises and falls. Thus, since a motor is not used for the advance and retreat of the valve body, the number of parts of the flow rate adjusting device can be reduced.

  The said structure WHEREIN: It is preferable that the said 1st biasing member and the said 2nd biasing member are arrange | positioned entirely in a storage chamber.

  According to the above configuration, since the entirety of the first urging member and the second urging member is disposed in the storage chamber, the first urging member and the second urging member have valve bodies on the fluid path. not exist. Therefore, when the fluid is pumped, the first urging member and the second urging member can be prevented from becoming an obstacle to the fluid flow.

  The said structure WHEREIN: It is preferable that the said valve body is entirely accommodated in the said storage chamber at the time of full opening.

  According to the above configuration, since the entire valve body is stored in the storage chamber, the valve body does not exist on the path of the fluid, and thus the flow rate adjusting device suppresses resistance by the valve body when the fluid is pumped. can do. Therefore, the fluid pumping efficiency is improved when the valve body is fully open.

  The said structure WHEREIN: It is preferable that a 2nd biasing member is a thermal expansion body from which a volume increases with a raise in temperature.

  According to the above configuration, as the temperature of the thermal expansion body increases, the volume of the thermal expansion body increases to urge the valve body against the urging force of the first urging member, and the valve body is stored in the storage chamber. I will store it.

  The said structure WHEREIN: It is preferable that the said housing is a pump housing of the said pump, and the said pump housing has a storage chamber and a pump chamber, and has an impeller which pumps a fluid in the said pump chamber.

  According to the above configuration, since the flow rate adjusting device is integrated with the pump housing, the size can be reduced.

  The said structure WHEREIN: It is preferable that the said storage chamber is formed so that the said pump chamber may be followed.

  According to the said structure, since a storage chamber is formed along a pump chamber, pump itself can be reduced in size.

  The said structure WHEREIN: It is preferable that the said valve body has a notch.

  According to the said structure, the fluid can flow from the notch of a valve body. Therefore, the notch part can adjust the pumping amount of the fluid in addition to the opening degree of the valve body. As a result, the flow rate adjusting device can easily pump the amount of fluid according to the demand.

It is a block diagram of the cooling system to which the water pump of this invention is applied. It is sectional drawing which shows the structure of a water pump. (A) is III-III sectional drawing of FIG. 2, (b) is an enlarged view of the A section of Fig.3 (a). It is sectional drawing in which the valve body of Fig.3 (a) was accommodated. It is a fragmentary fragmentary sectional view which shows the structure of the water pump of 2nd Embodiment in (a) of FIG. It is VI-VI sectional drawing of FIG. It is a principal part fragmentary sectional view which shows the structure of the water pump of 3rd Embodiment in (a) of FIG. It is principal part fragmentary sectional drawing which shows the structure of the water pump of 4th Embodiment in (a) of FIG. It is a principal part fragmentary sectional view which shows the structure of the water pump of 5th Embodiment in (a) of FIG. It is a principal part fragmentary sectional view which shows the structure of the water pump of 6th Embodiment in (a) of FIG. It is a principal part sectional view which shows the structure which the flow regulating device of FIG. 10 opened. It is a fragmentary fragmentary sectional view which shows the structure which the flow regulating device of FIG. 10 and the 2nd flow regulating device opened. It is a principal part fragmentary sectional view which shows the structure of the water pump of 7th Embodiment in (a) of FIG. (A) The principal part sectional drawing which shows the structure of 8th Embodiment in the XIVa-XIVA cross section of FIG. 13, (b) is the important part which shows the structure of 8th Embodiment in the XIVb-XIVb cross section of FIG. It is a fragmentary sectional view. (A) It is a principal part sectional view showing composition of a 9th embodiment in Drawing 14 (a), and (b) is a principal part sectional view showing a composition of a 9th embodiment in Drawing 14 (b). is there.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  The engine 1 having the cylinder head 9 and the cylinder block 17 outputs power by burning fuel such as gasoline. And since the engine 1 becomes high temperature by combustion at the time of a drive, it needs to cool.

  A water pump 2 (an example of a pump) shown below is used for cooling the engine 1.

  FIG. 1 is a block diagram of a cooling system to which a water pump 2 of the present invention is applied.

  As shown in FIG. 1, the cooling system includes a water pump 2 that pumps cooling water (an example of a fluid), a cooling water passage 3 through which the cooling water flows, a radiator 4 that radiates cooling water, and a temperature of the cooling water. And a thermostat 5 for switching the cooling water channel 3.

  The cooling water channel 3 is formed so as to pass through the inside of the engine 1. The cooling water passage 3 passes through the first flow passage 6 passing through the engine 1 from the water pump 2, the second flow passage 7 connecting the first flow passage 6 and the thermostat 5, the first flow passage 6 and the radiator 4. After that, a third flow path 8 that connects the thermostat 5 is provided.

  The engine 1 is cooled by exchanging heat with the cooling water by supplying cooling water to the first flow path 6 formed inside.

  The thermostat 5 allows the cooling water to flow through the second flow path 7 when the cooling water is at a low temperature. Thereafter, the thermostat 5 switches so that the cooling water flows through the third flow path 8 when the temperature of the cooling water reaches a predetermined temperature by exchanging heat (cooling) with the engine 1. The cooling water flowing through the third flow path 8 is cooled by the radiator 4.

  Next, the water pump 2 will be described with reference to FIG.

  FIG. 2 is a cross-sectional view showing the configuration of the water pump 2.

  As shown in FIG. 2, the water pump 2 mainly includes a pump housing 14 (having a suction port 11, a discharge port 12 (described in FIG. 3A), and a storage chamber 13 (described in FIG. 3A). An example of a housing), an impeller 15 that pumps cooling water, and a shaft 16 that rotates integrally with the impeller 15.

  As for the water pump 2, the pump housing 14 is fixed to one side surface of the cylinder block 17 of the engine 1, for example.

  As shown in FIG. 2, the pump housing 14 has a first housing member 21 fixed to the cylinder block 17 and a second housing member 22 fixed to the first housing member 21.

  The first housing member 21 is formed with a suction port 11 for sucking cooling water.

  The second housing member 22 is formed with a bearing portion 23 that rotatably supports the shaft 16.

  The bearing portion 23 is a through-hole that presents a cylindrical space at a substantially central portion of the second housing member 22. The shaft 16 is formed in a substantially cylindrical shape, and the outer diameter is substantially the same as the inner diameter of the bearing portion 23.

  In the following description, unless otherwise specified, the rotational axis direction of the shaft 16 is simply referred to as an axial direction, and the radial direction of the shaft 16 is simply referred to as a radial direction.

  Further, as shown in FIG. 2, a pump chamber for disposing the impeller 15 between the first housing member 21 and the second housing member 22 by fixing the first housing member 21 and the second housing member 22. 24 is formed. In other words, the impeller 15 is disposed in the pump chamber 24.

  The pump chamber 24 is formed in a substantially conical shape and is formed so as to communicate with the suction port 11. And when the pump chamber 24 projects from an axial direction, an inner wall exhibits a substantially involute curve.

  An impeller 15 that rotates integrally with the shaft 16 is press-fitted into one end portion of the shaft 16 on the first housing member 21 side. A pulley sheet 25 is press-fitted into the other end of the shaft 16.

  The impeller 15 has a substantially annular plate shape and includes wing portions 26 arranged radially on the surface on the first housing member 21 side.

  A driving pulley (not shown) is fixed to the pulley sheet 25. A timing belt (not shown) for transmitting power is attached to the drive pulley.

  The rotational driving force of the engine 1 is transmitted to the shaft 16 through a timing belt, a driving pulley, and a pulley sheet 25 (not shown). Thereby, when the engine 1 is driven, the water pump 2 impeller 15 rotates together with the shaft 16 so that the water pump 2 pumps the cooling water to the engine 1 and circulates the cooling water in the cooling water passage 3. Let

  Fig.3 (a) is III-III sectional drawing of FIG.

  As shown in FIG. 3A, the first housing member 21 further includes a discharge port 12 that discharges cooling water and a flow rate adjusting device 31.

  As the shaft 16 rotates, the impeller 15 rotates clockwise as indicated by an arrow W in FIG.

  The pump chamber 24 is formed along the impeller 15, and a draining portion 32 that guides cooling water flowing by the impeller 15 to the discharge port 12 is formed on the inner wall.

  The draining portion 32 is closest to the impeller 15 in the radial direction. Further, the inner wall of the pump chamber 24 is closest to the impeller 15 at the draining portion 32 in the radial direction, and exhibits an involute curve that moves away from the impeller 15 as the impeller 15 rotates.

  One of the discharge ports 12 communicates with the pump chamber 24, and the other communicates with the first flow path 6 of the cooling water channel 3.

  Next, the flow rate adjusting device 31 will be described with reference to FIGS.

  The flow rate adjusting device 31 is disposed in the storage chamber 13, the valve body 33 that adjusts the pumping amount of the cooling water by moving forward and backward from the storage chamber 13, and the valve body 33 protrudes from the storage chamber 13. A coil spring 34 (an example of a first urging member) that urges in such a manner, and a thermal expansion body 35 (a second urging member) that is disposed in the storage chamber 13 and urges the valve body 33 to be stored in the storage chamber 13. Example).

  As shown in FIG. 3A, the first housing member 21 is formed with a storage chamber 13 having a substantially plate-like space near the draining portion 32 on the outer diameter side of the pump chamber 24. Specifically, the storage chamber 13 is formed at the boundary position between the discharge port 12 and the pump chamber 24 in the first housing member 21. The storage chamber 13 presents an arcuate space along the pump chamber 24 when viewed from the axial direction.

  Here, let the direction along the pump chamber 24 of the storage chamber 13 be a longitudinal direction, and let the direction which cross | intersect a longitudinal direction be a transversal direction. The axial length of the storage chamber 13 is substantially the same as the axial length of the discharge port 12.

  Further, a communication portion 36 that connects the storage chamber 13 and the discharge port 12 is formed in the storage chamber 13.

  The communication portion 36 is formed at the end portion on the discharge port 12 side in the storage chamber 13 that can be formed at the boundary position between the discharge port 12 and the pump chamber 24 in the first housing member 21.

  Here, the thermal expansion body 35 can use wax, bimetal, or the like.

  And in the storage chamber 13, the valve body 33, the whole coil spring 34, and the whole thermal expansion body 35 are accommodated. Here, the valve element 33 is accommodated in the accommodating chamber 13 so as to be able to advance and retract. Further, the thermal expansion body 35 expands in volume as the temperature rises, and contracts in volume as the temperature falls.

  The valve body 33 has a protruding portion 41 at a base end 42 (described later) on the storage chamber 13 side, and has an arc shape along the storage chamber 13 when viewed from the axial direction. The valve body 33 is made of metal. The length in the longitudinal direction of the valve body 33 is shorter than the length in the longitudinal direction of the storage chamber 13, and the length in the short direction of the valve body 33 is substantially the same as the length in the radial direction of the communication portion 36. The axial length of the valve body 33 is substantially the same as the axial length of the storage chamber 13.

  The protruding portion 41 is formed at the base end 42 on the storage chamber 13 side in the longitudinal direction of the valve body 33 and protrudes toward the impeller 15 side (inner diameter side). The length of the protruding portion 41 in the radial direction is substantially the same as the short direction of the storage chamber 13.

  Here, in the valve body 33, one end where the protrusion 41 is formed is a base end 42, and the other end is a front end 43. In addition, a direction from the base end 42 toward the tip end 43 is a first direction, and a direction from the tip end 43 toward the base end 42 is a second direction.

  FIG.3 (b) is an enlarged view of the A section of Fig.3 (a).

  As shown in FIG. 3B, when the valve body 33 is disposed in the storage chamber 13, the protruding portion 41 comes into contact with the inner wall in the circumferential direction of the storage chamber 13. Therefore, the storage chamber 13 is partitioned into a first storage portion 44 on the discharge port 12 side and a second storage portion 45 by the protruding portion 41 of the valve body 33. Further, the first storage portion 44 and the second storage portion 45 are guided by the inner wall of the storage chamber 13 formed so that the valve body 33 extends along the circumferential direction, and the volume increases or decreases by moving in the circumferential direction. And if the volume of the 1st storage part 44 increases, the volume of the 2nd storage part 45 will decrease, and if the volume of the 1st storage part 44 decreases, the volume of the 2nd storage part will increase.

  As shown in FIG. 3A, the second storage portion 45 is provided with a coil spring 34 in an elastically deformed state. Therefore, the coil spring 34 biases the protrusion 41 toward the first direction by an elastic force. As a result, the valve element 33 protrudes in the first direction, and the tip end 43 comes into contact with the inner wall of the discharge port 12 to be in a closed state.

  As shown in FIG. 3B, a thermal expansion body 35 is disposed in the first storage portion 44 so as to be wrapped in a film 46 formed of an elastic body such as synthetic rubber.

  The thermal expansion body 35 has a property of increasing the volume with increasing temperature and decreasing the volume with decreasing temperature. And the volume of the thermal expansion body 35 of normal temperature is set so that it may become below the volume of the 1st accommodating part 44 in case the valve body 33 is valve-closing. Moreover, the thermal expansion body 35 is set so that when it becomes more than predetermined temperature, it will become more than the volume of the 1st accommodating part 44 in the case where the volume is closed.

  In the state where the elastic deformation does not occur, the volume inside the coating 46 is substantially the same as the volume of the thermal expansion body 35 at room temperature. When the volume of the thermal expansion body 35 increases as the temperature rises, the internal volume of the coating 46 is elastically deformed so as to be substantially the same as the volume of the thermal expansion pair 35.

  The film 46 is disposed so as to wrap the thermal expansion body 35. Therefore, even if the cooling water enters the storage chamber 13 through the communication portion 36, the thermal expansion body (liquid such as wax) 35 is prevented from being mixed with the cooling water or the like.

  Next, operation | movement of the water pump 2 of this embodiment is demonstrated.

  When the engine 1 starts driving, the rotational driving force of the engine 1 is transmitted to the shaft 16 via the timing belt, the driving pulley, and the pulley seat 25. As the shaft 16 rotates, the impeller 15 rotates in the arrow W direction. Here, the impeller 15 always keeps rotating in synchronism when the engine 1 is driven.

  When the impeller 15 starts rotating, the impeller 15 pumps the cooling water in the pump chamber 24 outward in the radial direction. Furthermore, the cooling water pumped toward the outside in the radial direction is guided to the discharge port 12 along the inner wall of the pump chamber 24 by the draining portion 32 of the pump chamber 24.

  Further, since the cooling water in the suction port 11 shown in FIG. 2 is pumped to the pump chamber 24 by the rotation of the impeller 15, the pressure of the cooling water in the pump chamber 24 increases.

  Next, operation | movement of the flow volume adjustment apparatus 31 of this embodiment is demonstrated.

  As shown in FIG. 3A, when the temperature of the cylinder block 17 is relatively low immediately after the engine 1 is started, the valve body 33 is configured such that the coil spring 34 biases the protruding portion 41 in the first direction. It protrudes from the storage chamber 13, and the tip 43 of the valve element 33 is in contact with the inner wall of the discharge port 12. Therefore, the flow rate adjusting device 31 is in a closed state by the valve body 33 dividing the discharge port 12 and the pump chamber 24.

  As a result, the cooling water in the pump chamber 24 is not discharged from the discharge port 12 by the valve body 33, so the pressure rises.

  When the engine 1 is driven, the temperature of the cylinder block 17 rises, and the heat of the cylinder block 17 is transmitted to the thermal expansion body 35 via the first housing member 21. And the volume of the thermal expansion body 35 in the 1st accommodating part 44 increases because the temperature of the thermal expansion body 35 rises.

  FIG. 4 is a cross-sectional view in which the valve element 33 of FIG.

  As shown in FIG. 4, when the volume of the thermal expansion body 35 is larger than the volume of the first storage portion 44 when the valve body 33 is closed, the thermal expansion body 35 resists the biasing force of the coil spring 34. The valve body 33 is urged in the second direction. In other words, the thermal expansion body 35 increases in volume as the temperature rises, so that the urging force increases, and urges the valve body 33 in the second direction against the urging force of the coil spring 34.

  At this time, when the valve body 33 moves in the second direction, the volume of the first storage portion 44 increases until it becomes substantially the same as the volume of the thermal expansion body 35. And the volume of the 2nd accommodating part 45 decreases substantially the same volume as the volume where the 1st accommodating part 44 increased.

  Specifically, the first storage portion 44 is configured by the inner wall of the storage chamber 13 and the valve body 33. And since the valve body 33 is stored in the storage chamber 13 so as to be able to advance and retract, when the volume of the thermal expansion body 35 in the first storage section 44 increases, the first storage section 44 has the valve body 33 in the second storage section. Increase volume by moving in the direction.

  In other words, the thermal expansion body 35 increases in volume as the temperature rises, so that the urging force in the second direction increases, and the valve body 33 starts to be stored in the storage chamber 13.

  Then, the valve body 33 starts to open by the urging force of the thermal expansion body 35 in the second direction.

  The cooling water whose pressure has been increased by the impeller 15 starts to be discharged from the discharge port 12 because the valve element 33 has started to open. In other words, the cooling water passes through the pump housing 14 and is pumped from the discharge port 12.

  Further, the cooling water pumped from the water pump 2 exchanges heat with the engine 1 through the cooling water passage 3.

  Therefore, the temperature of the cooling water rises by exchanging heat with the engine 1.

  When the flow rate adjusting device 31 is opened and the cooling water starts to flow, the thermal expansion body 35 exchanges heat with the cooling water in the pump chamber 24. Therefore, since the temperature of the thermal expansion body 35 rises with the rise in the temperature of the cooling water, the volume of the thermal expansion body 35 increases and the valve opening degree of the valve body 33 increases. As a result, the water pump 2 increases the amount of cooling water pumped.

  As shown in FIG. 4, when the valve opening degree of the valve body 33 is increased and the valve body 33 is fully opened, the entire valve body 33 is completely stored in the storage chamber 13.

According to the above embodiment, the following effects can be obtained.
(1) According to the above configuration, when the valve body 33 is in the fully closed state, the water pump 2 does not discharge cooling water because the pump chamber 24 and the discharge port 12 are separated by the valve body 33. Therefore, since the heat exchange by the cooling water is suppressed, the engine 1 can promote the warm-up of the engine 1 (2) According to the above configuration, when the valve body 33 is fully opened, Since the whole is completely stored in the storage chamber 13, the cooling water can reduce the flow resistance received from the valve element 33 when the impeller 15 pumps the cooling water. Therefore, the pumping efficiency of the water pump 2 is improved.
(3) According to the above configuration, the storage chamber 13 is formed along the substantially conical pump chamber 24. The storage chamber 13 formed along the pump chamber 24 is closer to the pump chamber 24 than the storage chamber 13 is formed in a substantially rectangular parallelepiped. Therefore, the first housing member 21 can be reduced in size because the distance between the pump chamber 24 and the storage chamber 13 is reduced.
(4) According to the above configuration, the valve opening degree of the valve body 33 is adjusted in accordance with the rise and fall of the temperature of the thermal expansion body 35. And the temperature of the thermal expansion body 35 rises and falls by heat exchange with cooling water. Further, the temperature of the cooling water rises in accordance with the temperature of the engine 1. In addition, the thermal expansion body 35 disposed in the storage chamber 13 formed along the pump chamber 24 has cooling water in the pump chamber 24 as compared with the case where the storage chamber 13 is formed in a substantially rectangular parallelepiped. Therefore, heat exchange with the cooling water is facilitated.

Therefore, the thermal expansion body 35 easily exchanges heat with the cooling water whose temperature has increased in accordance with the increase in the temperature of the engine 1. As a result, as the temperature of the engine 1 rises, the thermal expansion body 35 follows and the temperature rises. Therefore, the valve body 33 can adjust the valve opening degree with high responsiveness by the thermal expansion body 35.
(5) According to the above configuration, the coil spring 34 that moves the valve body 33 and the thermal expansion body 35 are disposed in the storage chamber 13. Therefore, the storage chamber 13 does not require a portion communicating with the outside. Therefore, there is no need for a seal member or the like for suppressing cooling water from leaking to the outside.

Moreover, since the whole coil spring 34 and the whole thermal expansion body 35 are arrange | positioned in the storage chamber 13, the coil spring 34 and the thermal expansion body 35 suppress that it becomes the obstruction | occlusion of cooling water when cooling water flows. can do.
(6) According to the said structure, since a thermal expansion body is wrapped in the membrane | film | coat, it can suppress that a thermal expansion body mixes with cooling water.
(Second Embodiment)
Hereinafter, 2nd Embodiment of the water pump 2 is described with reference to FIG.5 and FIG.6. The second embodiment differs from the first embodiment in the configuration of the discharge port 12a and the flow rate adjusting device 31a. For this reason, about the member structure which is common in 1st Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  FIG. 5 is a fragmentary partial cross-sectional view showing the configuration of the water pump according to the second embodiment in FIG.

  The storage chamber 13a has substantially the same shape as that of the first embodiment, and the axial length of the storage chamber 13a is longer than the axial length of the discharge port 12a. The axial length of the valve element 33a is substantially the same as the axial length of the storage chamber 13a.

  As shown in FIG. 5, at the boundary position between the discharge port 12a of the first housing member and the pump chamber 24, the first groove portion 51 that overlaps the locus of movement of the valve body 33a in the axial direction, and the tip of the valve body 33a The second groove portion 52 is formed in contact with the second groove portion 52.

  6 is a cross-sectional view taken along the line VI-VI in FIG.

  As shown in FIG. 6, the first groove 51 includes a first groove 51 a on the second housing member 22 side and a first groove 51 b on the cylinder block 17 side.

  The length of the first groove 51 in the axial direction is a length obtained by subtracting the length of the discharge port 12a in the axial direction from the length of the valve body 33a in the axial direction. In other words, the length obtained by adding the axial length of the first groove 51 and the axial length of the discharge port 12a is substantially the same as the axial length of the valve element 33a.

  Therefore, the valve body 33a protruding from the storage chamber 13a moves while being guided in the first groove 51 at both ends in the axial direction.

  The second groove portion 52 is formed in a region where the tip 43 of the valve element 33a contacts at the boundary position between the discharge port 12a and the pump chamber 24. The second groove 52 has an axial length that is substantially the same as the axial length of the valve element 33a.

  Therefore, the valve body 33a is closed when the tip 43 reaches the second groove 52.

  According to the said embodiment, in addition to the effect of (1) to (6) of 1st Embodiment, the effect shown below can be acquired.

  (7) According to the above configuration, both ends in the axial direction of the valve body 33 a protruding from the storage chamber 13 a are guided by the first groove portion 51. Therefore, the valve body 33a can move forward and backward stably and operate. Further, the valve body 33 a can receive the force received from the high-pressure cooling water in the pump chamber 24 by the first groove portion 51. As a result, the valve body 33a can reduce the load received from the cooling water.

(8) According to the above configuration, the valve element 33a is in the closed state with the tip 43 abutting against the second groove 52. Therefore, the valve body 33 a can receive the force received from the high-pressure cooling water in the pump chamber 24 by the second groove portion 52. As a result, the valve body 33a can reduce the load received from the cooling water.
(Third embodiment)
Hereinafter, a third embodiment of the water pump 2 will be described with reference to FIG. In addition, when compared with 1st Embodiment, 3rd Embodiment differs in the structure of the valve body 33b and the storage chamber 13b. For this reason, about the member structure which is common in 1st Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  FIG. 7 is a partial fragmentary sectional view showing the configuration of the water pump of the third embodiment in FIG.

  As shown in FIG. 7, in the valve body 33b, the tip 43 of the valve body 33b is formed with a second protrusion 61 that protrudes toward the impeller 15 side (inner diameter side) in the radial direction. It has substantially the same shape as the embodiment.

  The storage chamber 13 b is formed adjacent to the communication portion 36 and has a recess 62 for storing the second protrusion 61 when fully opened.

  The recess 62 has substantially the same length in the radial direction, the circumferential direction, and the axial direction as the length of the second protrusion 61 in the radial direction, the circumferential direction, and the axial direction.

  When fully opened, the second protrusion 61 is disposed in the recess 62 of the storage chamber 13b. Therefore, the entire valve body 33b is completely stored in the storage chamber 13b when fully opened.

According to the said embodiment, in addition to the effect of (1) to (6) of 1st Embodiment, the effect shown below can be acquired.
(9) According to the above configuration, the cooling water flowing along the inner wall of the pump chamber 24 presses the second protrusion 61 in the rotation direction of the impeller 15, so that the valve body 33 b is Receive direction force. Therefore, the valve body 33b is given a biasing force for opening the valve using water pressure other than the biasing force of the coil spring 34 and the biasing force of the thermal expansion body 35. As a result, the number of urging elements for urging the valve body 33b increases, so that the degree of freedom increases in adjusting the opening degree of the valve body 33b.

(Fourth embodiment)
Hereinafter, 4th Embodiment of the water pump 2 is described with reference to FIG. In addition, when compared with 3rd Embodiment, 4th Embodiment differs in the structure of the storage chamber 13c and the valve body 33c. For this reason, about the member structure which is common in 3rd Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  FIG. 8 is a fragmentary partial cross-sectional view showing the configuration of the water pump of the fourth embodiment in FIG.

  As shown in FIG. 8, in the first housing member, a storage chamber 13 c is formed in a region where the inner wall of the pump chamber 24 and the impeller 15 are farthest from each other on the outer diameter side of the pump chamber 24. Specifically, the storage chamber 13c is formed at a position facing the first embodiment at the boundary between the discharge port 12 and the pump chamber 24 in the first housing member 21.

  And the communication part 36 is formed in the discharge outlet side of the storage chamber 13c. And since the storage chamber 13c is formed in the position facing 1st Embodiment, the valve body 33c advances and retreats in the opposite direction with respect to 1st Embodiment. As a result, in the valve body 33c, the direction from the proximal end 42 toward the distal end 43 is defined as a second direction, and the direction from the distal end 43 toward the proximal end 42 is defined as a first direction.

  Similar to the first embodiment, a valve body 33c is disposed in the storage chamber 13c.

  And the 2nd protrusion part 61c which protrudes toward the impeller 15 side (inner diameter side) in the radial direction is formed in the front-end | tip 43 of the valve body 33c.

  The storage chamber 13c is formed with a recess 62c for storing the second protrusion 61c when fully opened.

  The concave portion 62c is formed in the vicinity of the communication portion 36 of the storage portion 13c, and the lengths in the radial direction, the circumferential direction, and the axial direction are substantially the same as the lengths in the radial direction, the circumferential direction, and the axial direction of the second protrusion 61c. .

  When fully opened, the second protrusion 61c is disposed in the recess 62c of the storage chamber 13c. Therefore, the entire valve body 33c is completely stored in the storage chamber 13c when fully opened.

According to the said embodiment, in addition to the effect of (1) to (6) of 1st Embodiment, the effect shown below can be acquired.
(10) According to the above configuration, the cooling water flowing along the inner wall of the pump chamber 24 presses the second projecting portion 61c in the rotation direction of the impeller 15, so that the valve body 33c has the first pressure due to the water pressure of the cooling water. Receive direction bias.

That is, the urging force for valve opening is applied to the valve body 33c using water pressure other than the urging force of the coil spring 34 and the urging force of the thermal expansion body 35. As a result, the number of urging elements that urge the valve body 33c is increased, and the degree of freedom is increased in adjusting the opening degree of the valve body 33c.
(Fifth embodiment)
Hereinafter, 5th Embodiment of the water pump 2 is described with reference to FIG. The fifth embodiment differs from the first embodiment in the configuration of the valve body 33d and the storage chamber 13d. For this reason, about the member structure which is common in 1st Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  FIG. 9 is a partial fragmentary sectional view showing the configuration of the water pump of the fifth embodiment in FIG.

  As shown in FIG. 9, the storage chamber 13 d is formed in the vicinity of the draining portion 32 and has an arc shape that does not follow the pump chamber 24 when viewed from the axial direction. Here, the arcuate direction of the storage chamber 13d is a longitudinal direction, and the direction intersecting the longitudinal direction is a short direction.

  The communication portion 36 is formed at the end on the discharge port 12 side in the storage chamber 13d. The axial length of the communication portion 36 is substantially the same as the axial length of the discharge port 12 and the storage chamber 13d.

  The valve body 33d is formed of an elastic body and has an arc shape along the storage chamber 13d when viewed from the axial direction. The valve body 33d has a length in the longitudinal direction shorter than the length in the longitudinal direction of the storage chamber 13d, the length in the short direction is substantially the same as the length in the radial direction of the communication portion 36, and the length in the axial direction. Is substantially the same as the axial length of the storage chamber 13d.

  Further, the valve body 33 d has a protruding portion 41.

  And the protrusion part 41 is formed in the edge part by the side of the storage chamber 13d in the longitudinal direction of the valve body 33d, and protrudes toward a radial direction outer side. And the length of the radial direction of the protrusion part 41 is substantially the same as the transversal direction of the storage chamber 13d.

  Next, operation | movement of the flow volume adjustment apparatus 31 of this embodiment is demonstrated.

  As shown in FIG. 9, when the temperature of the cylinder block 17 is low, such as immediately after the engine 1 is driven, the coil spring 34 biases the protrusion 41 in the first direction. Therefore, the valve element 33d is closed by the tip 43 abutting against the inner wall of the discharge port 12 and dividing the discharge port 12 and the pump chamber 24 as indicated by the dotted line IL in FIG. As a result, the cooling water in the pump chamber 24 is not discharged from the discharge port 12 and is retained in the pump chamber 24 by the valve body 33d, so that the pressure increases.

  Here, when the pressure of the cooling water in the pump chamber 24 becomes equal to or higher than a predetermined pressure, the valve body 33d formed of an elastic body is elastically deformed toward the flow direction of the cooling water by the water pressure. Therefore, the cooling water in the pump chamber 24 is pumped from the discharge port 12 and the pressure drops.

  The operation when the engine 1 is driven and the temperature of the cylinder block 17 rises is the same as in the first embodiment.

  According to the said embodiment, in addition to the effect of (1), (2), (5), (6) of 1st Embodiment, the effect shown below can be acquired.

(11) When the impeller 15 rotates while the cooling water is at a high pressure, the load received from the cooling water increases. According to the above configuration, when the pressure of the cooling water in the pump chamber 24 becomes equal to or higher than the predetermined pressure by the impeller 15, the valve body 33d, which is an elastic body, is deformed so that the cooling water in the pump chamber 24 12 is discharged. Therefore, it can suppress that the cooling water of the pump chamber 24 becomes more than predetermined pressure. As a result, since the impeller 15 is driven in a state where the cooling water is equal to or lower than a predetermined pressure, it is possible to reduce the load received when rotating.
(Sixth embodiment)
Hereinafter, a sixth embodiment of the water pump 2 will be described with reference to FIGS. 10 to 12. The sixth embodiment is different from the first embodiment in the configuration in which the second flow rate adjusting device 71 is newly provided. For this reason, about the member structure which is common in 1st Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  FIG. 10 is a partial fragmentary sectional view showing the configuration of the water pump of the sixth embodiment in FIG.

  As shown in FIG. 10, the first housing member 21 includes a flow rate adjustment device 31 and a second flow rate adjustment device 71 that are substantially the same as those in the first embodiment.

  Next, the second flow rate adjusting device 71 will be described with reference to FIG.

  The second flow rate adjusting device 71 is disposed in the second storage chamber 73, the second valve body 72 that adjusts the pumping amount of the cooling water by moving forward and backward from the second storage chamber 73, and the second storage chamber 73. A second coil spring 74 that urges the second valve body 72 to project from the second storage chamber 73 and the second storage chamber 73 are disposed so that the second valve body 72 is stored in the second storage chamber 73. And a second thermal expansion body 75 to be energized.

  As shown in FIG. 10, the second housing chamber 73 is formed in the first housing member 21 in a region where the impeller 15 and the inner wall of the pump chamber 24 are farthest from each other on the outer diameter side of the pump chamber 24. Specifically, the second storage chamber 73 is formed at a position facing the storage chamber 13 at the boundary position between the discharge port 12 and the pump chamber 24 in the first housing member 21. The second storage chamber 73 has an arc shape along the pump chamber 24 when viewed from the axial direction.

  Here, a direction along the pump chamber 24 of the second storage chamber 73 is defined as a second longitudinal direction, and a direction intersecting the second longitudinal direction is defined as a second short direction. The axial length of the second storage chamber 73 is substantially the same as the axial length of the discharge port 12.

  Further, the second storage chamber 73 includes a second communication portion 79 that is formed at the boundary position between the discharge port 12 and the pump chamber 24 in the first housing member 21 and communicates with the discharge port 12.

  The second communication part 79 communicates the discharge port 12 and the second storage chamber 73 at the end of the second storage chamber 73 on the discharge port 12 side. The length in the axial direction of the second communication portion 79 is substantially the same as the length in the axial direction of the discharge port 12 and the second storage chamber 73.

  In the second storage chamber 73, the second valve body 72, the entire second coil spring 74, and the entire second thermal expansion body 75 are stored.

  The 2nd valve body 72 has the 3rd protrusion part 78 and the penetration part 77 (an example of a notch part), and is arc shape along the 2nd storage chamber 73, when it sees from an axial direction. The second valve body 72 has a length in the second longitudinal direction shorter than a length in the second longitudinal direction of the second storage chamber 73, and a length in the second short direction in the radial direction of the second communication portion 79. The length in the axial direction is substantially the same as the length in the axial direction of the second storage chamber 73.

  The penetration part 77 is formed in a substantially central part when viewed from the radial direction. The penetrating portion 77 allows the pump chamber 24 and the discharge port 12 to communicate with each other even when the second valve body 72 is closed.

  The 3rd protrusion part 78 is formed in the edge part by the side of the 2nd storage chamber 73 in the 2nd longitudinal direction of the 2nd valve body 72, and protrudes toward the impeller 15 side (inner diameter side). The length of the third protrusion 78 in the radial direction is substantially the same as the second short direction of the second storage chamber 73.

  Here, the second valve body 72 has one end where the third protrusion 78 is formed as a second base end 82 and the other end as a second tip 81.

  Here, similarly to the first direction and the second direction of the valve body 33, the direction from the second distal end 81 toward the second proximal end 82 is defined as the first direction, and the direction from the second proximal end 82 toward the second distal end 81. Is the second direction.

  When the second valve body 72 is disposed in the second storage chamber 73, the third protrusion 78 comes into contact with the inner wall of the second storage chamber 73. Therefore, the second storage chamber 73 is partitioned into a third storage portion 83 on the discharge port 12 side and a fourth storage portion 84 by the third protrusion 78 of the second valve body 72. Further, the volume of the third storage portion 83 and the fourth storage portion 84 increases or decreases as the second valve body 72 moves.

  And if the volume of the 3rd storage part 83 increases, the volume of the 4th storage part 84 will decrease, and if the volume of the 3rd storage part 83 decreases, the volume of the 4th storage part 84 will increase. Here, when the valve body 33 and the second valve body 72 are closed, the first storage portion 44 and the third storage portion 83 have substantially the same volume, and the second storage portion 45 and the fourth storage portion 84. Are substantially the same volume.

  As shown in FIG. 10, a second coil spring 74 is disposed in the fourth storage portion 84 in an elastically deformed state. Therefore, the second coil spring 74 urges the third protrusion 78 toward the first direction by an elastic force. As a result, the second valve body 72 of the second flow rate adjusting device 71 protrudes in the second direction, and the second tip 81 comes into contact with the inner wall of the discharge port 12 so that the valve is closed.

  As in the first embodiment, a second thermal expansion body 75 is disposed in the third storage portion 83 so as to be wrapped in a second film (not shown) that is an elastic body. Therefore, even if cooling water enters, the second thermal expansion body is prevented from being mixed with cooling water or the like by the second film.

  The second thermal expansion body 75 has a property of greatly increasing or decreasing the volume as the temperature rises and falls. And the volume of the 2nd thermal expansion body 75 of normal temperature is set to the volume below the volume of the 3rd accommodating part 83 in case the 2nd valve body 72 is valve-closing, and the volume of the thermal expansion body 35.

  The water pump 2 performs the same operation as in the first embodiment.

  Next, operations of the flow rate adjusting device 31 and the second flow rate adjusting device 71 of the present embodiment will be described.

  As shown in FIG. 10, when the temperature of the cylinder block 17 is relatively low, such as immediately after the engine 1 is driven, the valve body 33 is moved from the storage chamber 13 by the coil spring 34 urging the protruding portion 41 in the first direction. Protruding. And the front-end | tip 43 of the valve body 33 contact | abuts to the inner wall of the discharge port 12, and the flow volume adjusting device 31 will be in a valve closing state by dividing the discharge port 12 and the pump chamber 24. FIG.

  Similarly, the second flow rate adjusting device 71 is also closed by the second tip 81 of the second valve body 72 contacting the inner wall of the discharge port 12 and dividing the discharge port 12 and the pump chamber 24.

  As a result, the cooling water in the pump chamber 24 is not discharged from the discharge port 12 by the valve body 33 and the second valve body 71, so the pressure rises.

  When the engine 1 is driven, the temperature of the cylinder block 17 rises, and the heat of the cylinder block 17 is transmitted to the thermal expansion body 35 and the second thermal expansion body 75 via the first housing member 21. And the volume of the thermal expansion body 35 in the 1st accommodating part 44 increases because the temperature of the thermal expansion body 35 rises. Similarly, when the temperature of the second thermal expansion body 75 increases, the volume of the second thermal expansion body 75 in the third storage portion 83 increases.

  As the volume of the thermal expansion body 35 increases, the valve body 33 starts to open as in the first embodiment. Here, since the volume of the second thermal expansion body 75 is smaller than that of the thermal expansion body 35, the second valve body 72 does not become larger than the third storage portion 83 when the valve is closed even if thermal expansion is performed. Therefore, the second valve body 72 remains in a closed state.

  FIG. 11 is a sectional view of the state in which the flow rate adjusting device 31 of FIG. 10 is fully opened.

  As shown in FIG. 11, when the valve body 33 is stored in the storage chamber 13 while the second valve body 72 is closed, the pump chamber 24 is cooled when the tip 43 of the valve body 33 exceeds the penetrating portion 77. Water is discharged from the discharge port 12 through the penetrating portion 77. The cooling water pumped from the water pump 2 exchanges heat with the engine 1 through the cooling water passage 3 and rises in temperature.

  When the flow rate adjusting device 31 is opened and cooling water begins to flow from the through portion 77, the temperature of the thermal expansion body 35 and the second thermal expansion body 75 rises due to heat exchange with the cooling water in the pump chamber 24. Then, as the temperature of the second thermal expansion body 75 increases, the volume of the second thermal expansion body 75 increases, and the second valve body 72 starts to open.

  Thereafter, as the temperature of the thermal expansion body 35 and the second thermal expansion body 75 further increases, the volume of the thermal expansion body 35 and the second thermal expansion body 75 increases, and the valve body 33 and the second valve body 72 are opened. The degree is increased. As a result, the water pump 2 increases the amount of cooling water pumped.

  FIG. 12 is a cross-sectional view of the state in which the flow rate adjustment device 31 and the second flow rate adjustment device 71 of FIG. 10 are fully opened.

  As shown in FIG. 12, when the valve opening degree of the valve body 33 and the second valve body 72 is increased and the valve body 33 and the second valve body 72 are fully opened, the whole of the valve body 33 and the second valve body 72 is the storage chamber 13 and the second storage. It is completely stored in the chamber 73.

According to the said embodiment, in addition to the effect of (1) to (6) of 1st Embodiment, the effect shown below can be acquired.
(12) In the flow rate adjusting device 31 and the second flow rate adjusting device 71, the opening degree of the valve body 33 and the second valve body 72 is determined as the volumes of the thermal expansion body 35 and the second thermal expansion body 75 increase. The Therefore, the opening degree of the valve body 33 and the second valve body 72 is substantially proportional to the temperature of the thermal expansion body 35 and the second thermal expansion body 75. According to the above configuration, the cooling water does not begin to flow until the opening degree of the valve body 33 exceeds the penetrating portion 77 of the second valve body 72.

That is, the flow rate of the cooling water can be adjusted by combining the flow rate adjustment device 31 and the second flow rate adjustment device 71. As a result, the water pump 2 can easily approximate the flow rate of the cooling water to the appropriate amount by the flow rate adjusting device 31 and the second flow rate adjusting device 71 with respect to the appropriate amount of the cooling water that changes as the temperature of the engine 1 increases. Become.
(Seventh embodiment)
Hereinafter, 7th Embodiment of the water pump 2 is described with reference to FIG. The seventh embodiment differs from the first embodiment in the configuration of the storage chamber 13f and the valve body 33f. For this reason, about the member structure which is common in 1st Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  FIG. 13 is a partial fragmentary sectional view showing the configuration of the water pump of the seventh embodiment in FIG.

  As shown in FIG. 13, the flow rate adjusting device 31 includes a valve body 33f, a storage chamber 13f that stores the valve body 33f, a coil spring 34 that urges the valve body 33f to protrude from the storage chamber 13f, and a valve body 33f. And a thermal expansion body 35 that urges the storage chamber 13f to store the thermal expansion body 35f.

  In the first housing member 21, a storage chamber 13 f that forms a substantially rectangular parallelepiped space is formed in the vicinity of the draining portion 32 of the pump chamber 24. The storage chamber 13f has a radial direction as a short direction and a direction perpendicular to the radial direction as a long direction.

  The axial length of the storage chamber 13f is substantially the same as the axial length of the discharge port 12. Furthermore, the storage chamber 13f includes a communication portion 36 that allows the storage chamber 13f and the discharge port 12 to communicate with each other.

  The communication portion 36 is formed at the end portion on the discharge port 12 side in the storage chamber 13 at the boundary position between the discharge port 12 and the pump chamber 24 in the first housing member 21. The axial length of the communication portion 36 is substantially the same as the axial length of the discharge port 12 and the storage chamber 13f.

  And the valve body 33f, the coil spring 34, and the thermal expansion body 35 are accommodated in the storage chamber 13f.

  The valve body 33f has a protrusion 41 and has a substantially rectangular parallelepiped shape. The length in the longitudinal direction of the valve body 33f is shorter than the length in the longitudinal direction of the storage chamber 13f, and the length in the short direction of the valve body 33f is substantially the same as the length in the radial direction of the communicating portion 36. The axial length of the body 33 is substantially the same as the axial length of the storage chamber 13f.

  As in the first embodiment, a thermal expansion body 35 is disposed in the first storage portion 44 so as to be wrapped in a film 46 formed of an elastic body, and in the second storage portion 45, The coil spring 34 is disposed in an elastically deformed state.

  As shown in FIG. 3A, the second storage portion 45 is provided with a coil spring 34 in an elastically deformed state. Therefore, the coil spring 34 biases the protrusion 41 toward the first direction by an elastic force.

  As shown in FIG. 13, the first housing member 21 is formed with a third groove portion 53 in a region that comes into contact with the tip 43 of the valve element 33 f when the valve is closed.

  The coil spring 34 biases the protrusion 41 toward the first direction by an elastic force. As a result, in the flow rate adjusting device 31, the tip 43 of the valve body 33f comes into contact with the third groove portion 53 on the inner wall of the discharge port 12 to close the valve.

  The thermal expansion body 35 has the property that the volume increases as the temperature rises, and the volume decreases as the temperature falls. And the volume of the thermal expansion body 35 of normal temperature is below the volume of the 1st accommodating part 44 in case the valve body 33f is valve-closing.

  The operations of the water pump 2 and the flow rate adjusting device 31 are the same as in the first embodiment.

According to the said embodiment, the effect of (1) (2) (5) and 2nd Embodiment (7) of 1st Embodiment can be acquired.
(Eighth embodiment)
Hereinafter, an eighth embodiment of the water pump 2 will be described with reference to FIG. In addition, when compared with 7th Embodiment, 8th Embodiment differs in the structure of the valve body 33g. For this reason, about the member structure which is common in 7th Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  FIG. 14A is a fragmentary partial cross-sectional view showing the configuration of the eighth embodiment in the XIVa-XIVa cross section of FIG.

  As shown in FIG. 14A, the valve body 33 g has a notch 91 formed at the tip 43.

  The notch 91 is formed at the tip 43 of the valve body 33g so as to cut off the corner of the valve body 33g. The length in the longitudinal direction of the notch 91 is substantially the same as the depth of the third groove 53. Therefore, the notch 91 is disposed in the third groove 53 when the valve element 33g is fully closed.

  Next, operation | movement of the flow volume adjustment apparatus 31 of this embodiment is demonstrated.

When the temperature of the cylinder block 17 is low, such as immediately after the engine 1 is driven, the valve body 33g is closed, so that the cooling water in the pump chamber 24 is not discharged from the discharge port 12.
When the engine 1 is driven, the temperature of the cylinder block 17 rises, the heat of the cylinder block 17 is conducted to the thermal expansion body 35, and the volume of the thermal expansion body 35 increases, so that the valve body 33g starts to open. .

  FIG. 14B is a partial fragmentary cross-sectional view showing the configuration of the eighth embodiment in the XIVb-XIVb cross section of FIG. 13.

  As shown in FIG. 14B, when the valve element 33 g starts to open, the cooling water in the pump chamber 24 is discharged from the discharge port 12 through the notch 91. Therefore, the temperature of the cooling water rises by exchanging heat with the engine 1.

  When the cooling water begins to flow through the notch 91, the thermal expansion body 35 exchanges heat with the cooling water in the pump chamber 24. Therefore, the temperature of the thermal expansion body 35 rises with an increase in the temperature of the cooling water, the volume of the thermal expansion body 35 increases, and the valve opening degree of the valve body 33g increases. As a result, the water pump 2 increases the amount of cooling water pumped.

  Thereafter, when the opening degree of the valve body 33g increases and the valve body 33g is fully opened, the entire valve body 33g including the notch 91 is completely stored in the storage chamber 13f. Is not arranged.

According to the said embodiment, in addition to the effect of (1) (2) (5) (6) and 2nd Embodiment (8) of 1st Embodiment, the following effect can be acquired.
(13) In the case of the seventh embodiment, when the valve element 33g starts to open, the distal end 43 of the valve element 33g is disposed in the third groove 53, so that the cooling water is supplied to the distal end of the valve element 33g. It does not begin to flow until 43 comes out of the third groove 53.

  According to the above configuration, the coolant starts to flow as soon as the valve element 33g starts to open due to the notch 91. That is, by forming the notch 91, the flow rate of the cooling water can be controlled except for the opening degree of the valve element 33g.

As a result, the water pump 2 can easily approximate the flow rate of the cooling water to the appropriate amount by the notch portion 91 with respect to the appropriate amount of the cooling water that changes as the temperature of the engine 1 increases.
(Ninth embodiment)
Hereinafter, a ninth embodiment of the water pump 2 will be described with reference to FIG. The ninth embodiment differs from the eighth embodiment in the configuration of the valve element 33h. For this reason, about the member structure which is common in 8th Embodiment, the same code | symbol is attached | subjected and description shall be abbreviate | omitted or simplified.

  Fig.15 (a) is principal part fragmentary sectional view which shows the structure of 9th Embodiment in Fig.14 (a).

  As shown in FIG. 15 (a), a notch 91h is formed in the valve body 33h.

  The notch portion 91h is a plurality of hole portions 92 (an example of a notch portion) formed at a substantially central portion of the discharge port 12 when fully closed.

  Next, operation | movement of the flow volume adjustment apparatus 31 of this embodiment is demonstrated.

  FIG.15 (b) is principal part fragmentary sectional view which shows the structure of 9th Embodiment in FIG.14 (b).

  As shown in FIG. 15B, when the temperature of the cylinder block 17 is relatively low, such as immediately after the engine 1 is driven, the valve element 33h is closed. However, cooling water is discharged from the notch 91h formed in the valve body 33h. Therefore, since the cooling water exchanges heat with the engine 1, the temperature rises.

  Since the cooling water flows through the hole 92 of the notch 91 h, the thermal expansion body 35 exchanges heat with the cooling water in the pump chamber 24. And since the temperature of the thermal expansion body 35 rises with a raise of the temperature of a cooling water, the volume of the thermal expansion body 35 increases and the valve opening degree of the valve body 33h becomes large. As a result, the water pump 2 increases the amount of cooling water pumped.

  In addition, when the valve body 33h is opened and the valve body 33h is fully opened, the entire valve body 33h is not stored on the cooling water path because it is completely stored in the storage chamber 13f.

According to the said embodiment, in addition to the effect of (2) (5) (6) and 2nd Embodiment (8) of 1st Embodiment, the following effect can be acquired.
(14) According to the above configuration, when the valve element 33h is fully closed, the cooling water is discharged from the discharge port 12 through the notch 91h. In the flow rate adjusting device 31, the thermal expansion body 35 exchanges heat with the cooling water immediately after the engine 1 is started.

  The thermal expansion body 35 is more likely to transmit the heat of the engine 1 to the thermal expansion body 35 via the cooling water than when the heat of the cylinder block 17 is transmitted to the thermal expansion body 35 via the first housing member 21. The temperature can be transmitted quickly.

Therefore, the temperature of the thermal expansion body 35 that can transmit the heat of the cylinder block 17 via the cooling water rises with high responsiveness according to the temperature of the cylinder block 17. As a result, the flow rate adjusting device 31 opens with good responsiveness as the temperature of the engine 1 increases.
(Modification)
In all the embodiments from the first embodiment to the ninth embodiment, the thermal expansion body 35 is the second urging member, but a bimetal may be used.

  In the first embodiment, the flow rate adjusting device 31 and the discharge port 12 are arranged one by one, but a plurality of the discharge ports 12 may be formed, and a plurality of the flow rate adjusting devices 31 may be arranged. The same applies to other embodiments.

  The cutout portion 91 of the eighth embodiment and the ninth embodiment can also be applied to the first to seventh embodiments.

  In all the embodiments from the first embodiment to the ninth embodiment, the thermal expansion body 35 is disposed in the first storage portion 44, but the heat formed so as to communicate with the first storage portion 44 when fully closed. An expansion chamber may be provided. The volume of the thermal expansion body 35 at room temperature is smaller than the volume obtained by adding the volume of the thermal expansion chamber and the volume of the first storage unit 44. Furthermore, since the volume of the thermal expansion body 35 increases due to the provision of the thermal expansion body chamber, the thermal expansion body 35 also increases in volume when the temperature rises. Therefore, the opening degree of the valve body 33 can be adjusted.

  In all the embodiments from the first embodiment to the ninth embodiment, the thermal expansion body 35 is wrapped in the film 46 to suppress mixing with the cooling water, but the film 46 is eliminated, and the storage chamber 13 and the valve body 33 are removed. The sealing member may be provided between the thermal expansion body 35 and the cooling water.

  In all the embodiments, the shape of the tip 42 may be a shape substantially corresponding to the shape of the communication portion 36. The valve body 33 forms substantially the same surface as the inner wall of the boundary position between the discharge port 12 and the pump chamber 24 when fully opened. Therefore, the water pump 2 can suppress the resistance when the cooling water at the time of full opening is pumped, so that the pump efficiency at the time of full opening can be improved.

  In all the embodiments, the coil spring 34 and the thermal expansion body 35 may not be stored entirely in the storage chamber 13.

1 Engine 2 Water pump (an example of a pump)
13 Storage chamber 14 Pump housing (an example of housing)
15 Impeller 16 Shaft 24 Pump chamber 31 Flow rate adjusting device 33 Valve element 34 Coil spring (an example of a first urging member)
35 thermal expansion body (an example of a second urging member)
77 Penetration part (an example of a notch)
91 Notch 92 Hole (an example of a notch)

Claims (8)

A pump for pumping fluid,
A housing through which the fluid passes and having a storage chamber;
A valve body that is disposed in the storage chamber and adjusts the pumping amount of the fluid by the pump by moving forward and backward from the storage chamber;
A first biasing member disposed in the storage chamber and biasing the valve body so as to protrude from the storage chamber;
A second biasing member disposed in the storage chamber and biasing the valve body so as to be stored in the storage chamber;
The second biasing member increases the biasing force as the temperature rises, and stores the valve body in the storage chamber against the biasing force of the first biasing member. The flow rate adjustment device according to claim 1, wherein the first urging member is entirely disposed in the storage chamber. The flow rate adjusting device according to claim 1, wherein the second urging member is entirely disposed in the storage chamber. The flow control device according to any one of claims 1 to 3, wherein the valve body is entirely stored in the storage chamber when fully opened. The flow regulating device according to any one of claims 1 to 4, wherein the second urging member is a thermal expansion body whose volume increases with an increase in temperature. The housing is a pump housing of the pump;
The pump housing has the storage chamber and the pump chamber,
The flow rate adjusting device according to any one of claims 1 to 5, further comprising an impeller that pumps fluid in the pump chamber. The flow rate adjusting device according to claim 6, wherein the storage chamber is formed along the pump chamber. The flow regulating device according to any one of claims 1 to 7, wherein the valve body has a notch.

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