JP2011214534A - Impeller in water pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance discharge performance in low-speed rotation of a water pump and to reduce the discharge performance in high-speed rotation, and to prevent a reduction in the discharge performance by other members.SOLUTION: An impeller in the water pump includes a storage case 1 with a plurality of long grooves 12a formed radially on a bottom disk 12, an impeller base 2 with blade sliding long holes 23 formed radially, which is fixed on the storage case 1, blade bodies 3 each with a slide shaft 33 arranged in the lower surface of a slide plate 32 in which a unit blade plate 31 is stood, and weights 4 each with notch long grooves 41 formed on both sides and a slide square shaft 43 sliding in the long groove 12a, which is arranged in its lower end. A plurality of the weights 4 stored in the storage case 1 resiliently constitute centrifugal force by compression springs 5. The slide plates 32 of the blade bodies 3 are arranged slidably correspondingly to the respective blade sliding long holes 23. The slide shafts 33 are arranged slidably in the notch long grooves 41 of the weights 4, The slide shafts 33 are configured to be positioned outside the impeller base 2 in a low rotation region of an engine by the resilient force of the compression springs 5.

Description

The present invention relates to an impeller in a water pump in which the discharge performance is increased at low speed rotation of the water pump and the discharge performance can be decreased at high speed rotation and the discharge performance is not deteriorated by other members.
In this specification, the discharge performance of the water pump means the discharge flow rate per unit rotation number, and the discharge flow rate of the water pump means the flow rate of cooling water discharged by the water pump per unit time. means.

  In recent years, there has been an increasing demand for lower fuel consumption of vehicles. In order to cope with this, there is an increasing demand for higher efficiency of each component mounted on the vehicle. Among the components mounted on the vehicle, the water pump is a component having an important function of adjusting the temperature of the engine, various electronic circuits, the heater core, etc., and maintaining the optimum temperature.

  There are two types of water pumps: mechanically driven water pumps and electrically driven water pumps. Electric drive type water pumps have been increasingly used in recent years, but since the price is expensive, there are more mechanical drive type water pumps in use at present.

  A large contribution to the discharge performance of the water pump is the size of the outer diameter of the blade member. Patent Document 1 is cited as a document in which the discharge performance of the pump is made variable by making the outer diameter of the blade member variable. Since the blade member 13 of Patent Document 1 is moved in the radial direction by the first wax type thermostat 15 and the second wax type thermostat 19, the water temperature of the cooling water is used as a trigger for the movement of the blade member 13. ing.

  Furthermore, the configuration of Patent Document 1 is as follows. A disc-shaped disk member 11 is disposed on the base side of the blade member 13. On the outer periphery of the disk member 11, radial cutout grooves 11A are provided at intervals of 90 degrees. A rectangular parallelepiped blade member 13 is slidably provided in the cutout groove 11A in the radial direction. A rod-shaped guide rod 13 </ b> A is provided on the inner peripheral side of the blade member 13 and reaches the vicinity of the center of the pump impeller member 10. An annular chamber 11C, which is an internal space, is formed at the center of the disk member 11, and a first wax type thermostat 15 is built therein.

  A columnar space 11B is formed in the vicinity of the side surface in the rotational direction of the cutout groove 11A of the disk member 11, and a lever member 16 having the columnar space 11B as a rotation center is provided. A return spring 17 is attached to the center of rotation of the lever member 16 to urge the blade member 13 engaged with the distal end portion 16B of the lever member 16 in the central direction (radially inner peripheral side). The cover member 12 is disposed so as to be combined with the disk member 11 on the opposite side of the blade member 13 in the axial direction. A second wax type thermostat 19 is also built in the center of the cover member 12.

  In such a configuration, when the coolant temperature is low, the wax contracts due to the biasing force of the return spring 17 because the wax contracts in both the first wax type thermostat 15 and the second wax type thermostat 19. The outer diameter of the blade member 13 is reduced. Thereby, the discharge performance of the water pump when the coolant temperature is low can be lowered. This reduces unnecessary work when the coolant temperature is low.

  On the contrary, in such a configuration, when the coolant temperature is high, the wax expands in both the first wax type thermostat 15 and the second wax type thermostat 19, so that the wax is larger than the urging force of the return spring 17. , The blade member 13 moves to the radially outer peripheral side, and the outer diameter of the blade member 13 increases. Thereby, the discharge performance of the pump when the coolant temperature is high can be increased. This suppresses overheating, which is a concern when the coolant temperature is high.

  In Patent Document 1, when the coolant temperature of the engine is low, the pump discharge performance is reduced to reduce unnecessary work, and when the engine coolant temperature is high, the pump discharge performance is increased to overheat. Is suppressed. However, the following problems remain in Patent Document 1. That is, in Patent Document 1, there is a serious problem that it is related to the coolant temperature and not related to the engine speed.

  In general, when changing the pump discharge performance using the engine speed as a trigger, the pump discharge flow rate itself is small in the low engine speed range, so the pump discharge performance is increased to ensure the coolant flow rate. However, since the pump discharge flow rate itself is large in the high engine speed region, it is considered better to lower the pump discharge performance in order to suppress cavitation.

  By the way, since centrifugal force acts on the blade member 13 in Patent Document 1, generally speaking, since the centrifugal force is small in the low engine speed region, the blade member 13 is in the central direction (radially inner peripheral side). Since the centrifugal force is large in the high engine speed region, the blade member 13 moves to the radially outer peripheral side. Then, the discharge performance of the pump is further lowered when the engine speed is low, and the discharge performance of the pump is further enhanced when the engine speed is high. There are drawbacks.

JP-A-4-3221797

  For this reason, the problem (technical problem or purpose) to be solved by the present invention is that the centrifugal performance acts, but the discharge performance is increased in the low engine speed range, and the high engine speed is in the high engine speed range. Then, it is to realize the development of a water pump impeller that lowers the discharge performance and operates reliably.

  Accordingly, as a result of intensive researches to solve the above-mentioned problems, the inventor clarified the invention of claim 1 as a storage case in which a plurality of long grooves in the radial direction are formed on the bottom disk and a plurality of blades in the radial direction. An impeller base formed with a sliding long hole and fixed on the storage case, a blade body provided with a sliding shaft on the lower surface of the sliding plate on which the unit blade plate is erected, and a notch long groove on both sides And a plurality of weights are stored in the storage case, and the weights and the weights are radiated in a radial direction by centrifugal force. A compression spring is interposed between the sliding side and the outer side of the storage case, and the sliding plate of the blade body is slidably provided corresponding to each blade sliding long hole of the impeller base, and The sliding shaft slides in the notch long groove of the weight In the water pump, wherein the sliding shaft is positioned outside the impeller base in a low rotation region of the engine by the elastic force of the compression spring. By using an impeller, the above problems were solved.

  According to a second aspect of the present invention, in the first aspect of the present invention, in the high rotation region of the engine, the sliding angular shaft slides radially outward in the long groove against the elastic force of the compression spring applied to the weight. In addition, the impeller in the water pump is characterized in that the sliding plate of the blade body is configured to slide inside the blade sliding long hole of the impeller base. did. According to a third aspect of the present invention, in the first or second aspect, the angle between the notched long grooves is smaller than the angle between adjacent blade sliding long holes of the impeller base. The above-described problem is solved by using the impeller in the water pump as a feature.

  In the first aspect of the invention, the impeller can be positioned on the radially outer peripheral side in the low engine speed region to increase the discharge performance, and in the high engine speed region, the impeller can be operated in the direction opposite to the normal direction. The discharge performance of the water pump can be lowered by moving it to a certain radially inner side. Thereby, suppression of cavitation and reduction of water pump waste work can be achieved.

  Further, in the present invention, it is constituted only by the impeller part, and it is not necessary to change the water pump part other than the impeller part at all, so that there is an advantage that adaptation to an existing product can be easily performed. There is an advantage that the discharge performance is not lowered by other members. Further, in the inventions of claims 2 and 3, the same effects as in claim 1 are obtained.

(A) is a perspective view of the present invention in which the entire blade body has the minimum diameter, (B) is a cross-sectional view of the present invention in which the entire blade body has the maximum diameter and the left and right sides are different, (C) FIG. 4 is a cross-sectional view of a main part in a state where left and right blades are loosely inserted into weight portions. (A) is an exploded perspective view of the present invention, (B) is a cross-sectional view taken along the line PP of (A). (A) is a plan view of the present invention in the low rotation region, (B) is a state diagram in which the compression spring acts in (A) and the weight does not move, (C) is a plan view of the present invention in the high rotation region, (D) is the state figure in which the weight which opposes the compression spring in (C) is moving. (A) is a perspective view of a main member of the present invention, (B) is an operation state diagram of the present invention in a low rotation region, and (C) is an operation state diagram of the present invention in a high rotation region. (A) is an operation state diagram of the present invention in the low rotation region, (B) is an operation state diagram of the present invention immediately after (A), and (C) is a schematic diagram showing an operation state of the present invention.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIGS. 1 and 2 are embodiments of the present invention. The impeller of the water pump of the present invention mainly includes a storage case 1, an impeller base 2, a blade body 3, a weight 4, and a compression spring 5. In the storage case 1, a bottom disc 12 is formed outward from the lower end of the central boss portion 11, and a rising portion 13 is formed on the outermost periphery of the bottom disc 12. The boss portion 11 and the rising portion 13 are formed at the same height. The bottom disk 12 is formed thick and has a plurality of (three in the embodiment) long grooves 12a formed radially.

  The weight 4 and the compression spring 5 are accommodated in the accommodation locations of the boss portion 11, the bottom disc 12, and the rising portion 13. A rotating shaft of a water pump is inserted and fixed in the boss portion 11. As a means for fixing the hole portion 11a of the boss portion 11 and the rotating shaft, as with the impeller base, keying or press-fitting is performed. However, in the case of keying, a key groove is formed in the hole portion 11a of the boss portion 11. Sometimes provided.

  The impeller base 2 has a bulging portion 21 at the center and a disc portion 22 around the bulging portion 21, and has the same shape as the storage case 1 in plan view. A blade sliding long hole 23 is formed in the disk portion 22 in the radial direction. The blade body 3 is configured to slide through the blade sliding long hole 23. In the embodiment, the six blade bodies 3 are respectively provided in the six blade sliding long holes 23 whose circumferences are equally spaced. The sliding distance of the blade body 3 is configured as a stroke S as shown in FIGS. 1 (A) and 1 (B). The impeller base 2 is placed on the upper side of the storage case 1 and serves as a lid.

  In the blade body 3, a unit blade plate 31 that is inclined is integrally formed on an upper surface of a rectangular sliding plate 32. The sliding plate 32 is slidably provided in the blade sliding long hole 23. Specifically, the sliding side portions 32 a and 32 a on both sides of the sliding plate 32 are configured to be slidable (slidable) on the sliding side walls 23 a and 23 a of the blade sliding long hole 23. Further, a sliding shaft 33 is integrally formed on the lower surface of the sliding plate 32.

  The weight 4 is a member that slides in a radial direction by centrifugal force according to the rotation of the impeller. Specifically, it has a shape of a deformation 3. The notch long grooves 41 and 41 are provided symmetrically and have a square shape when seen in a plan view. The angle β of the notched long grooves 41 and 41 viewed in a plan view is used. In the embodiment, it is 45 degrees. A recess 42 is formed in the center of the two notched sliding grooves 41, 41, and the compression spring 5 is interposed therein. A sliding angle shaft 43 having a square cross section is provided on the lower side of the center of the weight 4. The sliding angle shaft 43 slides in the long groove 12 a of the bottom disc 12.

  The operation of the present invention will be described. First, since the elastic force (biasing force) of the compression spring 5 is larger than the centrifugal force of the weight 4 in the low engine speed region, the weight 4 is positioned on the radially inner peripheral side (center side). [See FIG. 1 (B), FIG. 3 (A) and (B)]. At the same time, the blade body 3 is positioned on the radially outer side corresponding to the weight 4 (see FIGS. 1B, 3A, and 3B). That is, the outer circle of the entire blade body 3 has a maximum diameter. Since the discharge flow rate of the water pump is originally small in the region where the engine speed is low, the lack of cooling water can be solved by increasing the discharge performance of the water pump as in the present invention.

  In addition, when the engine speed is high, the centrifugal force of the weight 4 is larger than the elastic force (biasing force) of the compression spring 5, and the weight 4 is positioned on the radially outer side [FIG. 3 (B) to (C) state]. Then, when the notch long groove 41 having the angle β of the weight 4 moves upward in FIG. 3B, the sliding shaft 33 of the blade body 3 moves downward. In this operation, the blade body 3 integrated with the sliding shaft 33 moves inward through the blade sliding long hole 23 of the impeller base 2 configured to be slidable at an angle α.

This point will be described in detail. As shown in FIG. 5A, the outer shape of the slide shaft 33 is considerably large, and the weight 4 into which the slide shaft 33 is loosely inserted is radially outer peripheral side. (Practically upward in FIG. 5 (A) by centrifugal force), a downward force P _β is obtained due to the notched long groove 41 at the angle β, but here it is fixed to the sliding shaft 33. Since the sliding shaft 33 of the blade body 3 is configured to be slidable at the angle α, the downward force P _α is applied to the lower side of the angle α direction, and the state shown in FIG. 5B is obtained. further moving the weight 4 in the radial direction outer peripheral side (in fact upwards movement in FIG. 5 (B) by centrifugal force), the vane body 3, the sliding shaft 33 the angle alpha becomes downward force P _alpha Go in the direction. When this state is simplified, the state is as shown in FIG.

In addition, when such a state is simplified, in FIG. 4A, when the weight 4 moves to the side facing the centrifugal force, the blade body 3 simultaneously moves to the near side. That is, as shown in FIG. 4 (B), the elastic force (biasing force) of the compression spring 5 is larger than the centrifugal force of the weight 4 when the engine speed is low, and the blade 3 Is located on the radially outer peripheral side. At this time, the distance from the center of the impeller base 2 to the sliding shaft 33 is L _{0 at the} maximum (see FIG. 4B). In the high rotation region, the centrifugal force of the weight 4 becomes larger than the elastic force (biasing force) of the compression spring 5, and the weight 4 is positioned on the radially outer peripheral side [FIG. B) to (C) state].

  At the same time, the sliding shaft 33 is moved downward in the β angle, and the blade body 3 is moved in the downward direction of the angle α, so that the state shown in FIG. 4C is reached, and the blade body 3 moves to the center side. The entire outer circle has the smallest diameter. At this time, the distance from the center of the impeller base 2 to the sliding shaft 33 is a small distance L ′ (see FIG. 4C). In this way, in the high engine speed range, cavitation can be avoided by reducing the discharge performance of the water pump.

  In order to change the desired rotation speed that changes the discharge performance of the water pump, it is only necessary to change the weight of the weight 4 or change the strength of the spring of the compression spring 5. That is, by appropriately changing the weight of the weight 4 and the strength of the spring of the compression spring 5, the discharge performance of the water pump can be easily changed.

DESCRIPTION OF SYMBOLS 1 ... Storage case, 12 ... Bottom disk, 12a ... Long groove, 2 ... Impeller base,
23 ... blade sliding long hole, 3 ... blade body, 31 ... unit blade plate, 32 ... sliding plate, 33 ... sliding shaft,
4 ... Weight, 41 ... Notch long groove, 43 ... Sliding angular axis, 5 ... Compression spring.

Claims (3)

  A storage case in which a plurality of long grooves are formed on the bottom disk in the radial direction, an impeller base in which a plurality of blade sliding long holes are formed in the radial direction and fixed on the storage case, and a unit blade are erected. A blade body provided with a sliding shaft on the lower surface of the sliding plate, and a weight formed with a notched long groove on both sides and a sliding angle shaft sliding on the lower groove at the lower end, A plurality of weights are stored in the storage case, and a compression spring is interposed between the weight and a side where the weight slides in a radial direction by centrifugal force, and an outer side of the storage case, and the sliding plate of the blade body Is slidably provided corresponding to each blade sliding long hole of the impeller base, and the sliding shaft is provided so as to be slidable in the notch long groove of the weight. The above-mentioned sliding in the low rotation area of the engine by force Impeller but in water pump characterized by comprising it has been configured to be positioned outside of the impeller base.   In Claim 1, in the high rotation area of the engine, the sliding angular axis slides radially outward in the long groove against the elastic force of the compression spring applied to the weight, and the blade body The impeller in a water pump, wherein the sliding plate is configured to slide inside the blade sliding long hole of the impeller base.   3. The impeller in a water pump according to claim 1, wherein the angle between the notched long grooves is smaller than the angle between adjacent blade sliding long holes of the impeller base. .

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