JP2002127736A - Fluid heating device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a novel fluid heating technique of obtaining a high heat generation effect of a fluid in a turbine pump type fluid heating device. SOLUTION: The heating pump 10 consists of a pump housing 11, a rotor 20 accommodated in the pump housing 11, etc. An annular water channel 18 facing against the side face of the rotor 20 is formed in the pump housing 11. A flat plate-like protrusion 26 projecting toward the inside of the water channel 18 protrudes radially in the outer peripheral face of a boss part 19 constituting the inner peripheral surface 18b of the water channel 18. The protrusion 26 suppresses the cooling water from flowing backward on the inner periphery of the water channel 18 as a passage from a high pressure side to a low pressure side to enhance the heating effect of the cooling water.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid heating apparatus for heating a fluid, and more particularly to a technique for rationally heating a fluid in a turbine pump type fluid heating apparatus.

[0002]

2. Description of the Related Art For example, U.S. Pat. No. 3,720,372 discloses a turbine pump type fluid heating device. This type of fluid heating device raises (heats) the temperature of the fluid by using a pump for pumping the fluid and a fluid restrictor on the discharge side of the pump. In the pump housing, a rotor having a plurality of blades radially protruding on the outer periphery is arranged, and when the rotor is rotated, fluid sucked from the suction port is formed in the housing on both sides of the rotor. The pressure is sent to the high pressure side while increasing the pressure while taking up a helical flow path by the secondary flow (axial rotation) in the formed annular water path, and the brake is applied by the throttle valve provided on the discharge side. It is configured. Thereby, in the process of discharging the fluid sucked from the suction port through the discharge port, the power applied to the rotor is:
It is converted into pumping work to pump the fluid and heat resulting from power loss to the fluid.

[0003]

The fluid heating technique according to the above configuration can provide both a fluid transfer function for transferring a fluid and a fluid heating function for heating a fluid in a simple configuration. Is extremely effective. However, in the fluid heating apparatus having the above-described configuration, a fluid heating technique in which the structure of the pump itself is further devised has not been established in order to more efficiently heat the fluid. Therefore, the present inventors believe that if a technique for a pump structure in consideration of heating of a fluid can be established, the fluid can be heated rationally, and attention has been paid to the structure of this type of pump. The influence of the shape and the like of each member constituting on the heating of the fluid was studied diligently. As a result, the present inventors have a correlation between the shape of the water passage of the housing through which the fluid flows and the amount of heat generated by the temperature rise of the fluid, and configure the water channel into a suitable shape in consideration of the amount of heat generated by the fluid. By doing so, we succeeded in finding that a high heat generation effect of the fluid can be obtained.

Accordingly, an object of the present invention is to provide a novel fluid heating technique capable of obtaining a high heat generation effect of a fluid in a turbine pump type fluid heating device.

[0005]

In order to achieve the above object, a fluid heating device according to the present invention has a configuration as described in each of the claims. Here, the terms described in each claim and the detailed description of the invention are interpreted as follows unless otherwise limited. (1) The "fluid" includes not only a heat reducing material (cooling water, lubricating oil, etc.) or hydraulic oil but also various fluids capable of conducting heat.

According to the first aspect of the present invention, in the turbine pump type fluid heating device, a dam member for suppressing fluid flow is provided on an inner peripheral side of an annular water passage formed in the housing. . When the fluid is sent to the high pressure side while being pressurized in the water channel by the rotation of the rotor,
The inner peripheral side of the water channel has a lower pressure and a lower peripheral velocity than the outer peripheral side. Therefore, there is a possibility that a so-called “backflow” occurs in which a part of the fluid on the high pressure side returns to the low pressure side through the inner peripheral side of the water channel. Therefore, the present inventors conducted an experiment for measuring, for example, a change in the calorific value of the cooling liquid in a case where the shape of the housing is such that a dam member is provided in an annular water channel, and the case where the dam member is not provided. As a result of the test, it was confirmed that the heat generation effect of the coolant was enhanced as compared with the case where no damming member was provided. That is, claim 1
According to the invention described in (1), by providing a dam member on the inner peripheral side of the annular water passage formed in the housing, it is possible to suppress the cooling water on the high pressure side from flowing back through the inner peripheral side of the water passage. In addition, the heat generation performance of the cooling water can be improved.

[0007] In this case, as described in claim 2, in the cross-sectional shape in the water channel, it is preferable that the wall surface continuous with the inner peripheral surface and the outer peripheral surface is formed by an arcuate curved surface. Such setting of the curved surface shape can reduce the stagnation of the fluid flowing in the water channel and obtain a smooth flow.

[0008] In addition, the dam member installed in the water channel,
As described in claim 3, it is preferable that the protrusion is a protrusion radially protruding from the outer peripheral surface of the boss portion of the housing forming the inner peripheral wall surface of the water channel into the water channel. As described in item 4, it is preferable that the width is set to approximately １ ／ of the width of the water channel. According to the measurement test, it has been confirmed that a suitable heat generating effect can be obtained by adopting the above configuration.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The structure of a fluid heating device according to the present invention will be described below with reference to FIGS. Here, FIG. 1 is a diagram showing a schematic configuration of a coolant circulation circuit in a vehicle air conditioning system. FIG. 2 is a cross-sectional view showing a heating pump of the fluid heating device according to the present embodiment, and FIG.
FIG. 3 is a sectional view taken along line II-III. FIG. 4 is a front view of the rear housing, and FIG. 5 is a sectional view taken along line VV of FIG.

As shown in FIG. 1, a vehicle engine E is
Water jacket 50 and its water jacket 5
And a water pump 52 for pumping a coolant (engine coolant) to the water pump 52. The cooling liquid is, for example, an antifreeze composed of water and ethylene glycol. In addition to the engine E, the circulating circuit of the coolant is provided by a radiator 6, a thermostat valve 7, a heater core 8, an electromagnetic valve 8a, a check valve 9, a fluid heating device H, and a plurality of pipes 1 to 5 connecting them. It is configured. These plumbing
It is roughly divided into three pipes 1, 2, 3 on the downstream side of the water jacket 50, and two pipes 4, 5 on the upstream side of the water jacket 50. The pipe 4 constitutes a path on the inflow side that returns to the water pump 52 via the radiator 6 and the thermostat valve 7. The pipe 5 constitutes an inflow-side path returning to the water pump 52 via the electromagnetic valve 8 a and the heater core 8. The pipe 1 constitutes an inflow path from the water jacket 50 to the thermostat valve 7. That is, the thermostat valve 7 is provided at a branch point between the pipe 1 and the pipe 4. The pipe 2 is connected to the water jacket 50 via the check valve 9 via the two pipes 4,
The path on the outflow side which is connected to 5 is formed. Pipes 2 and 3
There is a parallel relationship between the water jacket 50 and the pipes 4 and 5.

The water pump 52 is operatively connected to a crankshaft (output shaft) of the engine E via a V-belt or the like, and operates using the driving force of the engine E. A water pump 52 disposed near the inlet of the water jacket 50 pumps the coolant returning via the pipes 1, 4, 5 into the water jacket 50. This pumping force is the main driving force when the coolant flows through the circulation circuit.

The radiator 6 functions as a heat exchanger for radiating heat from the coolant to the outside air. The thermostat valve 7 detects the temperature of the coolant flowing from the engine E via the pipe 1 or 4, and connects one of the pipes 1 and 4 to the water pump 52 according to the detected temperature. That is, when the temperature detected by the thermostat valve 7 is lower than the set temperature (for example, 80 ° C.), the pipe 1 is connected to the water pump 52.
To short circuit the coolant circulation circuit to increase the temperature of the coolant due to engine waste heat. On the other hand, the thermostat valve 7
If the detected temperature is equal to or higher than the set temperature, the pipe 4 is connected to the water pump 52 to stop the short circuit through the pipe 1 and to lower the temperature of the coolant. The radiator 6,
The thermostat valve 7 and the pipe 4 constitute an engine cooling circuit for selectively cooling the coolant together with other circuit elements and the pipe.

The heater core 8 functions as a heating heat exchanger for heating the air in the vehicle cabin by using the amount of heat of the coolant flowing through the pipe 5. The electromagnetic valve 8a is an ON / OFF valve (simple on-off valve) that controls the supply and cutoff of the coolant from the engine E to the heater core 8 according to the state of cooling and heating of the vehicle air conditioning system. In addition, the heater core 8, the electromagnetic valve 8a, and the piping 5 constitute a heating circuit of the vehicle air-conditioning system together with other circuit elements and piping.

The check valve 9 allows only the flow in the outflow direction from the water jacket 50 toward the pipes 4 and 5.
The check valve 9 mainly opens when the amount of outflow through the pipe 3 is greatly reduced under the condition that the outflow through the pipe 1 is stopped by the thermostat valve 7 (that is, when the radiator 6 is effective), The circulation of the coolant in the pipes 4 and / or 5 is always ensured.

As shown in FIG. 1, a turbine pump type fluid heating device H has a heating pump 10 and a throttle valve 40 (corresponding to the fluid throttle means of the present invention) provided in series along a pipe 3. ). Then, by the cooperation of both, the two capabilities are simultaneously (or selectively) while balancing the functions of the pump and the function of the heating device.
Can be demonstrated.

Next, the internal structure of the heating pump 10 will be described in detail with reference to FIGS. As shown in FIGS. 2 to 5, the heating pump 10 includes a pump housing 11, a rotor 20 rotating in the pump housing 11, and the like. Pump housing 1
Reference numeral 1 denotes three front, center, and rear housings 11F, 11C, and 11R that are divided into three parts in the axial direction. The center housing 11C has a suction port 13 for sucking a coolant as a fluid of the present invention. A discharge port 14 for discharging the coolant through the rotor 20 is provided.
In the center housing 11C and the rear housing 11R, a stripper 15 for separating the suction port 13 and the discharge port 14 is provided.
Is provided.

The pump housing 11 is provided with a working chamber 25 for accommodating the rotor 20.
Is connected to the upstream side of the pipe 3 via the suction port 13, and is connected to the downstream portion (or the throttle valve 40) of the pipe 3 via the discharge port 14. In the working chamber 25, an integrated drive shaft 22 and rotor 20 are provided. The drive shaft 22 is rotatably supported by the bearing 12. One end of the drive shaft 22 penetrates the center and the front housings 11C and 11F, and a pulley 16 is spline-fitted to the penetrating end outside the front housing 11F.
7, the pulley 16 is fixed to a V-belt (FIG. 1).
) Is operatively connected to the crankshaft (output shaft) of the engine E through the like.

The rotor 20 has a rotor main body 24 formed in a disk shape, and a plurality of blade members (in the present embodiment) are arranged on both outer peripheral side surfaces (peripheral surfaces) of the rotor main body 24 at equal intervals. (In the embodiment, 14 blades). The blade 21 has a rectangular plate-like shape extending radially from the rotation center side of the rotor main body 24, and a concave groove 23 is formed between the blades 21.

An annular water passage 18 is formed in the pump housing 11 so as to face the side surface of the rotor 20. This water channel 18 constitutes a part of the working chamber 25,
As shown in FIGS. 3 and 5, the inner peripheral surface 18b and the outer peripheral surface 1
8c and a bottom surface 18a, and is formed in a semicircular cross section. That is, the wall surface which is the bottom surface 18a of the water channel 18 and is continuous with the inner peripheral surface 18b and the outer peripheral surface 18c is formed in an arcuate curved surface, and the smoothness of the flow is ensured. As shown in FIG. 4, a plurality of plate-like projections 26 are provided at predetermined intervals in the circumferential direction on the outer peripheral surface of a boss portion (supporting portion of the drive shaft 22) 19 which forms the inner peripheral surface 18b of the water channel 18. Are protruded integrally. The projection 26 radially protrudes from the outer peripheral surface of the boss toward the water channel 18 and corresponds to a dam member according to the present invention. In the present embodiment, as shown in FIG. 5, the height H of the protrusion 26 is set to approximately １ ／ of the channel width B.

In the heating pump 10 having the above structure, the driving shaft 22 and the rotor 20 are driven by using the driving force of the engine E.
Is rotated, so that the suction port 1
The coolant sucked in from the outlet 3 flows around the working chamber 25 and
4 is discharged. That is, the annular water passage 18 facing the rotor 20 by the rotation of the rotor 20 and the rotor 2
A flow (secondary vortex) as shown in FIG. 3 is formed in a region formed by the zero groove 23. Then, as the flow formed in each groove 23 and the main flow of the coolant in the water channel 18 are repeated, the pressure of the coolant is gradually amplified.
In this sense, the heating pump 10 is
It has the same fluid transfer function as 2 and can serve as an auxiliary pump that assists the water pump 52. In addition,
When the heating pump 10 is operated, a gap is formed between the stripper 15 of the pump housing 11 and the groove 23 of the rotor 20, and a relatively high pressure discharge port 14 is formed through the gap. Internal leakage (internal leakage) of the cooling liquid occurs toward the appropriate suction port 13, thereby promoting heat generation in the heating pump 10.

Further, the heating pump 10 has a fluid heating function in addition to the fluid transfer function. In other words, the heating pump 10 secures a gap that becomes a flow resistance between members or parts constituting the flow path of the coolant, for example, by minimizing the difference between the inner diameter of the working chamber 25 and the outer diameter of the rotor 20. As a result, when the rotor 20 rotates, pump work is given to the coolant in the working chamber 25, and heat is generated due to an increase in internal energy of the coolant. Therefore, the power applied from the pulley 16 to the drive shaft 22 and the rotor 20 is converted into the work that the rotor 20 does for forcibly pumping the coolant and the heat that results from the power loss. Also, by restricting the opening degree of the throttle valve 40 provided downstream of the discharge port 14 of the heating pump 10 so as to make the cooling liquid difficult to flow, a braking force is applied to the cooling liquid pressure-fed by the rotor 20 and cooling is performed. The heat generation effect of the liquid can be enhanced. Therefore,
The cooling liquid can be heated by the heating pump 10.

Since the fluid transfer function and the fluid heating function are opposite to each other, the coolant can be heated to a higher temperature by increasing the degree of throttle of the coolant by the throttle valve 40. The transfer rate of the cooling liquid decreases. On the other hand, when the degree of throttle of the coolant by the throttle valve 40 is reduced, a relatively large amount of coolant can be transferred.
In this case, the temperature of the coolant does not easily rise.

The present inventors have considered that there is some correlation between the shape of the water passage 18 formed in the pump housing 11 and the heat generation effect in the fluid heating device that operates as described above. Specifically, when the cooling water is sent to the high pressure side while being pressurized in the water passage 18 by the rotation of the rotor 20, the pressure on the inner peripheral side of the water passage 18 is lower than that on the outer peripheral side, and the peripheral speed is also lower. Therefore, the cooling water flowing through the water channel 18 has a lower momentum on the inner peripheral side than on the outer peripheral side, and as a result,
It was considered that a so-called "backflow" occurred in which a part of the fluid on the high-pressure side returned to the low-pressure side through the inner peripheral side of the water passage 18, which hindered the heat generation effect of the cooling water.

In order to prevent the above-mentioned "backflow", a projection 26 as a blocking member for suppressing the flow of the cooling water is provided on the inner peripheral surface 18b of the water passage 18 in a direction crossing the water passage 18, By changing the protrusion height H (see FIG. 5) (four patterns) and changing the rotation speed of the rotor 20, a test for repeating the measurement of the calorific value and the pressure of the coolant was performed, and FIG. 6 and FIG. The result as shown in FIG. Here, FIG. 6 shows the heat value [kW] of the coolant and the rotation speed [r /
7] is a graph showing the correlation between the pressure H of the coolant and the rotation speed [r / min] of the rotor 20, and FIG.
7 is a graph shown for each projection height H. In FIGS. 6 and 7, a plot is plotted when the projection height H of the projection 26 with respect to the channel width B (see FIG. 5) is 1/8, a plot is plotted when 1/4, and a plot is plotted when it is 1/2.プ ロ ッ ト plot, △ plot for 1/1, and １ plot for no protrusion.

As shown in FIG. 6, the heat value of the cooling water increases as the rotation speed of the rotor 20 increases. And
Of the four patterns, when the projection height H of the projection 26 with respect to the channel width B is 1/8, the heat generation effect of the coolant is the highest and 1
In the case of ４ and １ ／, the heat generation effect is slightly higher than in the case without the protrusion, and in the case of 1/1, the heat generation effect is rather reduced as compared with the case without the protrusion.

As shown in FIG. 7, the pressure of the cooling water increases as the rotation speed of the rotor 20 increases. In the four patterns, when the protrusion height H of the protrusion 26 with respect to the channel width B is 1/8, when the protrusion height is 1/4 and when the protrusion height H is 1/2, the pressurizing effect is higher than when there is no protrusion. That is, in the case of 1/1, the boosting effect is lower than in the case where there is no protrusion.

As described above, according to the present embodiment, a plurality of flat plates as shown in FIGS. 4 and 5 are provided on the outer peripheral surface of the boss portion 19 of the pump housing 11 constituting the inner peripheral surface 18b of the water passage 18. By projecting the projections 26 radially,
The “backflow” of the cooling water from the high pressure side to the low pressure side can be suppressed without obstructing the secondary flow in the water channel 18, and the heat generation effect and the pressure increasing effect of the cooling water can be enhanced. as a result,
The performance as a fluid heating device, that is, both the fluid transfer function and the fluid heating function can be improved. Further, in the present embodiment, since the bottom surface 18a of the water channel 18 is formed by an arc-shaped curved surface, stagnation of the cooling water in the water channel 18 can be reduced, and a smooth fluid flow can be obtained. In addition, since the projection 26 protruding from the outer periphery of the boss 19 also functions as a rib of the pump housing 11, the wall of the pump housing 11 can be made thinner. Further, the projection 26 can be formed at the same time when the pump housing 11 is molded, and in that case,
Since it has a rectangular flat plate shape, the releasability is not impaired.

It should be noted that the present invention is not limited to only the above-described embodiment, and various modifications are possible. For example, in the embodiment, the case where the protrusion 26 is formed in the shape of a substantially rectangular flat plate and protrudes radially from the outer peripheral surface of the boss portion 19 is not limited to this. For example, FIG. As shown in FIG. 9, the projection 26 is projected from the high pressure side toward the low pressure side so as to be inclined.
A similar effect can be expected even if the shape of No. 6 is formed into a curved shape. Also, regarding the number and thickness of the projections 26,
8 may be changed while taking care not to reduce the effective area. Further, in the embodiment, the case where a cooling liquid composed of water and ethylene glycol is used as the fluid has been described, but various fluids capable of conducting heat may be used instead of the cooling liquid.

[0029]

As described in detail above, according to the present invention,
In a turbine pump type fluid heating device, a novel fluid heating technology capable of obtaining a high heat generation effect of fluid can be realized.

[Brief description of the drawings]

FIG. 1 is a diagram showing a schematic configuration of a coolant circulation circuit in a vehicle air conditioning system.

FIG. 2 is a cross-sectional view showing a heating pump of the fluid heating device according to one embodiment of the present invention.

FIG. 3 is a sectional view taken along line III-III in FIG. 2;

FIG. 4 is a front view of a rear housing.

FIG. 5 is a sectional view taken along line VV of FIG. 4;

FIG. 6 is a graph showing a correlation between a heat value of a coolant and a rotation speed of a rotor for each protrusion height of a protrusion.

FIG. 7 shows the correlation between the pressure of the coolant and the rotation speed of the rotor.
It is a graph shown for every projection height of a projection.

FIG. 8 is an explanatory diagram showing a modification example regarding the shape of a projection.

FIG. 9 is an explanatory view showing another modified example of the shape of the projection.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Heating pump 11 Pump housing 13 Suction port 14 Discharge port 18 Water path 18a Bottom surface 19 Boss 20 Rotor 21 Blade 24 Rotor main body 25 Working chamber 26 Projection (dam member)

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Tatsuyuki Hoshino 2-1-1 Toyota-cho, Kariya-shi, Aichi F-term in Toyota Industries Corporation (reference) 3H034 AA01 AA15 BB01 CC03 DD05 EE02

Claims (4)

[Claims] A rotor having a plurality of blades on an outer periphery thereof; a housing rotatably housing the rotor; an annular water passage formed in the housing so as to face a side surface of the rotor; A fluid restricting means for restricting the fluid flowing from the suction port and flowing through the water channel at the discharge side, wherein a fluid flow is suppressed to an inner peripheral side of the water channel. A fluid heating device comprising a dam member. 2. The fluid heating device according to claim 1, wherein in a cross-sectional shape of the water channel, a wall surface continuous with an inner peripheral surface and an outer peripheral surface is formed by an arcuate curved surface. Heating equipment. 3. The fluid heating device according to claim 1, wherein the dam member radially protrudes from an outer peripheral surface of a boss portion of a housing constituting an inner peripheral wall surface of the water channel into the water channel. Fluid heating device, characterized in that it is a projection. 4. The fluid heating device according to claim 3, wherein the protrusion height of the projection is set to approximately ８ of the width of the water channel.