JPH1142932A - Heat generator for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a viscous fluid from being deteriorated due to overheating by autonomously adjusting the amount of heat generation without using any external mechanism in a heat generator for vehicle. SOLUTION: A heating chamber 5 and a radiation chamber (water jacket) 6 enclosing the heating chamber 5 are formed in a heater housing. The heating chamber 5 includes a first rotor 13 fixed to the rear end part of a rotatable drive shaft 12 and a second rotor 16 as a shearing means fixed to the front end part of a driven shaft 15, and is filled with silicon oil as viscous fluid. Also the viscous fluid present between both rotors 13 and 16 functions as a fluid joint medium, and forms a fluid clutch together with both rotors 13 and 16. By the function of such a fluid clutch, a torque transmission from the first rotor 13 to the second rotor 16 is adjusted according to a variation in viscosity of the viscous fluid, and the amount of shearing heat generation by the second rotor 13 is feed back-controlled.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a housing, a drive shaft rotatably provided in the housing, a heat generating chamber and a heat radiating chamber defined in the housing, and a heat generating chamber disposed in the heat generating chamber. Shearing means driven based on power supply via the drive shaft, and generates heat by shearing the viscous fluid in the heating chamber by the shearing means,
The present invention relates to a vehicle heat generator for exchanging the heat with a circulating fluid flowing through the radiating chamber.

[0002]

U.S. Pat. No. 4,454,861 discloses a domestic heating system incorporating a heater based on fluid friction. The outline of this heating system is described below in FIG. This will be described with reference to the reference number shown in FIG.

[0003] A housing 74 of the heater 70 is formed in a cylindrical shape, and a drum 72 (corresponding to a shearing means) is rotatably provided inside the housing 74. Further, the housing 7
A jacket 80 is provided so as to surround the outer periphery of No. 4. A cylindrical space 82 is formed between the jacket 80 and the housing 74, and the space 82 has an entrance 85.
(For example, hot water) flowing toward the outlet 86 from the outlet. The inner peripheral wall of the housing 74 and the drum 72
Between the inlet 89 and the outlet 9 is formed in the clearance area.
A fluid (eg, water) flowing toward zero is circulated.
In the heater 70, when the drum 72 is forcibly rotated in the housing 74 by the drive of the motor 78, the fluid (water) interposed between the inner peripheral wall of the housing and the outer peripheral portion of the drum.
Is sheared by the drum 72 and is heated based on fluid friction. The heated fluid is supplied to a piping system 94 through an outlet 90, and is returned to the inlet 89 in a cold state after being supplied to home heating and other uses. Also,
Part of the heat generated in the clearance area is transmitted to the hot water flowing through the cylindrical space 82 via the housing wall. The hot water reheated by this heat is supplied to the outlet 8
It is supplied to the domestic piping system via 6 and used for home use as described above.

[0004]

In the above-mentioned conventional heater, water, which is a fluid to be sheared, is heated using fluid friction caused by mechanically forced shearing of liquid (water). But,
Water itself is a very low viscosity fluid and does not inherently easily generate fluid frictional heat with a small amount of mechanical shear. Therefore, the conventional heater employs a complicated structure in which intricate grooves are formed in the outer peripheral portion of the drum and the inner peripheral wall of the housing in order to dramatically improve the shearing efficiency. In addition, in order to secure a sufficient heat generation amount, in order to expand the clearance area as a heat generation chamber, it is inevitably required to increase the size of the drum and the motor for driving the drum.

In a home heating system, such a complicated and large heater may be put into practical use.
However, such a complicated and large heater cannot be used as it is as an auxiliary heat source for a vehicle. Therefore, there is a demand for a heat generator that has a higher shear heat generation efficiency and can be reduced in size.

From such a viewpoint, a heat generator for a vehicle in which a heat generating chamber and a heat radiating chamber are separately formed in a housing of the heat generator and a single rotor is arranged as a shearing means in the heat generating chamber. Has been proposed. In this heat generator for a vehicle, a high-viscosity fluid such as silicone oil is used as a fluid to be sheared to be filled into the heat-generating chamber, and heat generated by shearing the high-viscosity fluid by the rotor is circulated through the heat-radiating chamber. The heat is exchanged with a fluid (for example, engine cooling water), and the heated circulating fluid is used for heating a vehicle or the like.

However, when, for example, a silicone oil is used as the fluid to be sheared (a viscous fluid), it is necessary to take measures to keep the temperature at the time of heat generation from exceeding its heat resistance limit. Generally, silicone oil has its own heat resistant temperature (for example, 250
When the temperature exceeds the temperature (° C.), overheating occurs, which causes a problem that thermal degradation occurs and viscosity is reduced, and the shear heat generation efficiency is rather lowered. Since the temperature of the fluid to be sheared tends to increase as the rotational speed of the rotor as the shearing means increases, if the power transmission from an external drive source (for example, a vehicle engine) to the rotor is mechanically controlled, the viscosity of the viscous fluid is reduced. It is also possible to prevent the situation of overheating due to overshearing. However, mechanically controlling the power transmission to the rotor, i.e.
If a mechanism for controlling the rotation speed of the rotor is provided separately, the power transmission system that connects the heat generator for the vehicle and the external drive source becomes mechanically complicated or large, and a small heat source that can be mounted on the vehicle. The purpose of providing a generator is dismissed.

[0008] An object of the present invention is to make it possible to autonomously control the amount of heat generation without using an external mechanism, and as a result, to maintain the heat generation performance as needed while preventing the viscous fluid from deteriorating due to overheating. It is an object of the present invention to provide a variable-capacity heat generator for a vehicle that can be effectively used.

[0009]

According to a first aspect of the present invention, there is provided a housing, a drive shaft rotatably provided in the housing, a heat generating chamber and a heat radiating chamber defined in the housing, and the heat generating chamber. Shearing means disposed in the room and driven based on power supply via the drive shaft, and generating heat by shearing the viscous fluid in the heating chamber by the shearing means, and generating the heat by the shearing means. A vehicle heat generator for exchanging heat with a circulating fluid flowing through a heat radiating chamber, comprising: a first rotor rotatably provided in the heat generating chamber and operatively connected to the drive shaft; and the drive shaft and the first rotor. And a second rotor as the shearing means rotatably provided in the heat generating chamber without being mechanically connected, wherein the first rotor and the second rotor are provided between these two rotors. With an intervening viscous fluid A vehicular heat generator, which comprises a fluid clutch.

According to this heat generator, since the first rotor is operatively connected to the drive shaft, externally supplied power is transmitted to the first rotor via the drive shaft. The second rotor is
The drive shaft and the first rotor are not mechanically connected, but have an indirect connection with the first rotor via the above-described fluid clutch. Therefore, the rotation torque of the first rotor is transmitted to the second rotor via the viscous fluid interposed between the two rotors. As a result, the second rotor as the shearing means is driven to generate shear heat.

The viscosity of the viscous fluid changes in accordance with the change in the amount of heat generated by the shearing of the second rotor.
The torque transmission from the rotor to the second rotor is adjusted,
The amount of heat generated by shearing by the rotor is feedback-controlled.
That is, when the temperature of the viscous fluid in the heating chamber increases due to the shearing action of the second rotor, the viscosity of the viscous fluid tends to decrease. Accordingly, the torque transmission capability of the fluid clutch is reduced, and the shearing action of the second rotor is also reduced. as a result,
The amount of shear heat generated by the second rotor tends to be suppressed, and the situation of overheating of the viscous fluid is avoided. Further, when the shear heat generation amount of the second rotor is suppressed and the temperature of the viscous fluid decreases and the viscosity tends to increase, the torque transmission capability of the fluid clutch increases, and the shearing action of the second rotor increases again.

As described above, in the present invention, since the fluid clutch having two rotors as components is provided in the heat generating chamber containing the viscous fluid, the amount of heat generated by shearing by the second rotor and the torque transmission capability by the fluid clutch is reduced. A reciprocal function relationship is established, and the heat generation amount of the heat generator can be adjusted autonomously.

In the first aspect, "without mechanical connection" literally means that the second rotor is not mechanically and directly connected to the drive shaft and the first rotor. This means that the viscous fluid interposed between the two rotors becomes a fluid coupling medium, and the two rotors can indirectly form a connected state only through the fluid coupling medium.

According to a second aspect of the present invention, in the vehicle heat generator according to the first aspect, the first rotor and the second rotor each have opposing surfaces, and these opposing surfaces are provided in the heat generating chamber. It is characterized in that, at a predetermined interval, a coupling region in which a viscous fluid is interposed is formed between the opposed surfaces.

In this case, a part of the viscous fluid contained in the heat generating chamber is interposed in the coupling region between the opposing surfaces of the first and second rotors. This viscous fluid functions as a fluid coupling medium in the fluid clutch. The distance between the opposing surfaces affects the maximum value of the torque transmission capability of the fluid clutch. For this reason, according to this configuration, it is possible to set the torque transmission capability of the fluid clutch by appropriately adjusting the distance between the opposing surfaces.

According to a third aspect of the present invention, in the vehicle heat generator according to the first or second aspect, the second rotor has a cylindrical shape, and an outer peripheral surface of the cylindrical second rotor;
A predetermined clearance is provided between the outer peripheral surface and the opposing peripheral surface of the heat generating chamber.

According to this configuration, the viscous fluid is interposed in the clearance between the outer peripheral surface of the cylindrical second rotor and the peripheral surface of the heating chamber. The viscous fluid of the clearance is supplied to the cylindrical outer peripheral surface (movable surface) of the rotating second rotor.
A strong shearing action is generated based on a relative speed difference between the heat generating chamber and the peripheral surface (stationary surface), and heat is generated by fluid friction. In this heat generator, the clearance region is the main shear heat generation region.

In this specification, "the rotor has a cylindrical shape" means that the axial length (total length) of the rotor is larger than the radius of the rotor, and the interior of the rotor is hollow. It has nothing to do with being a solid body.

According to a fourth aspect of the present invention, in the vehicle heat generator according to the third aspect, the heat radiation chamber is provided so as to surround the predetermined clearance along an outer peripheral surface of the second rotor. It is characterized by being.

According to this arrangement, the predetermined clearance area along the outer peripheral surface of the second rotor, which is the main shear heat generation area, and the heat radiating chamber are closest to each other, so that the viscous fluid in the heat generating chamber changes to the circulating fluid in the heat radiating chamber. Increases the heat exchange efficiency.

According to a fifth aspect of the present invention, in the vehicle heat generator according to any one of the first to fourth aspects, a pulley is provided at an end of the drive shaft, and the drive shaft and the drive shaft are connected to each other. The first rotor is directly driven by an external drive source via a power transmission belt wound around the pulley.

Since the heat generator of the present invention is capable of autonomously controlling the amount of heat generated as described above, it does not require a special mechanism for power supply adjustment outside the heat generator. Therefore, it is possible to receive the power supply from the external drive source with the simplest configuration (the pulley and the power transmission belt) as described in claim 5.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION

(Embodiment 1) Hereinafter, Embodiment 1 in which the present invention is embodied in a heat generator incorporated in a vehicle heating device will be described with reference to FIGS.

As shown in FIG. 1, the vehicle heat generator of the first embodiment includes a central housing 1, a stator 2 disposed inside the central housing 1, a front housing 3 and a rear housing 4. The stator 2 is a cylindrical body having an annular cross section, and the central housing 1 is formed to accommodate the cylindrical stator 2 therein. As shown in FIG. 1, a front housing 3 and a rear housing 4 are provided in the central housing 1 and the stator 2 so as to seal the front and rear openings.
Are joined via annular sealing members 3a, 4a. The central housing 1, the stator 2, and the front and rear housings 3 and 4 are mutually fastened and fixed by a plurality of through bolts (not shown), and constitute a housing as a whole.

A heating chamber 5 is defined inside the stator 2 to which the front and rear housings 3 and 4 are joined.
A water jacket 6 as a heat radiating chamber is provided between the outer peripheral surface of the stator 2 and the inner peripheral surface of the central housing 1.
Are formed. Therefore, the central housing 1, the stator 2, and the front and rear housings 3, 4 are also positioned as partition members for partitioning the heat generating chamber 5 and the water jacket (radiating chamber) 6 in the housing. In the present embodiment, the water jacket (heat radiating chamber) 6 is arranged so as to surround the heat generating chamber 5.

FIG. 2 is a developed view in which the stator 2 is cut open along one side extending in the longitudinal direction. 1 and 2
As shown in FIG. 2, a plurality of ridges 7 are provided on the outer peripheral surface of the stator 2. Each ridge 7 extends in the circumferential direction of the stator 2. When the stator 2 is disposed in the central housing 1, these ridges 7 come into close contact with the inner peripheral surface of the central housing 1 and extend along the circumferential direction of the stator 2 as shown in FIG. A meandering distribution path P is set in the water jacket 6. in this way,
The ridge 7 sets a circulation path P of the circulating fluid in the water jacket 6 and functions as a guide wall for guiding the circulating fluid flowing therethrough.

The central housing 1 has a water jacket 6
The central housing 1 is provided with an entrance communication hole 9 and an exit communication hole 10. As shown in FIG. 2, the entrance communication holes 9 and the exit communication holes 10 are arranged at respective positions corresponding to the start point and the end point of the distribution path P. The inlet communication hole 9 functions as a circulating fluid inlet for the heat radiating chamber, and the outlet communication hole 10 functions as a circulating fluid outlet for the heat radiating chamber.

Although only a part is shown in FIG.
The inner wall of the flow path P on the outer peripheral surface has a plurality of grooves 8 along the direction in which the flow path P extends (the direction in which the circulating fluid flows).
Are formed. FIG. 3 shows a sectional shape and the like of the groove 8. Each groove 8 formed on the inner wall of the circulation path P is
This is provided to efficiently transfer heat from the water jacket 6 to the water jacket 6. The groove 8 extending along the flow path P may be formed also on the inner peripheral wall side of the central housing 1.

As shown in FIG. 1, a drive shaft 12 is rotatably supported on the front housing 3 via a front bearing 11. The front bearing 11 is a bearing device with a seal, is interposed between the inner peripheral surface of the front housing 3 and the outer peripheral surface of the drive shaft 12, and seals the front of the heat generating chamber 5. The front end of the drive shaft 12 projects outside the front housing 3, and the rear end of the drive shaft 12 projects into the heat generating chamber 5. A driven shaft 15 is rotatably supported by the rear housing 4 via a rear bearing 14. The rear bearing 14 is a bearing device with a seal, is interposed between the inner peripheral surface of the rear housing 4 and the outer peripheral surface of the driven shaft 15, and seals the rear of the heat generating chamber 5. The front end of the driven shaft 15 projects into the heat generating chamber 5. Drive shaft 12 and driven shaft 1
5 are arranged so as to be aligned on the same rotation axis C.

A first rotor 13 and a second rotor 16 are accommodated in the heat generating chamber 5 provided as a liquid-tight internal space. The first rotor 13 is press-fitted and fixed to the rear end of the drive shaft 12 and rotates integrally with the drive shaft 12. The first rotor 13 is formed in a disk shape, and its radius r1 is the entire length (length in the axial direction) as schematically shown in FIG.
It is longer than L1 (r1> L1). On the other hand, FIG.
As shown in (2), the second rotor 16 is press-fitted and fixed to the front end of the driven shaft 15, and rotates together with the driven shaft 15.
The second rotor 16 is formed in a cylindrical shape, and as schematically shown in FIG. 4, its radius r2 is shorter than the total length (length in the axial direction) L2 (r2 <L2).

Further, in the heating chamber 5, the first rotor 1
The rear end face 13a of the third rotor 3 and the front end face 16a of the second rotor 16 face each other in parallel at a predetermined interval h1. The diameter (2 × r1) of the first rotor rear end face 13a is set smaller than the diameter (2 × r2) of the second rotor front end face 16a. A coupling area 17 is formed between the opposing surfaces 13a and 16a. As described later, a viscous fluid is interposed in the coupling region 17.

Further, the cylindrical outer peripheral surface of the second rotor 16
It faces the inner peripheral surface of the stator 2 surrounding it at a predetermined interval, and a minute clearance h2 is formed between the two (see FIG. 4).

In the heat generating chamber 5 as a liquid-tight internal space,
The required amount is filled with silicone oil as a viscous fluid. The filling amount Vf of this silicone oil is
80% to 90% of the free space volume Vc obtained by subtracting the member occupied volume (the volume occupied by the drive shaft 12, the driven shaft 15, the first rotor 13 and the second rotor 16 in the heat generating chamber 5) from the calculated internal volume It is decided to be about. The reason why the oil filling amount Vf is limited to about 80 to 90% of the free space volume Vc is to take into consideration the expansion of the viscous fluid when the temperature rises due to heat generation.

Silicone oil is interposed in the coupling area 17, and the viscous fluid in the coupling area 17 functions as a fluid coupling medium. That is, coupling area 1
The viscous fluid in 7 together with the first rotor 13 and the second rotor 16 constitutes a "fluid clutch" or "fluid coupling means".

As shown in FIG. 1, a screw hole 12a is formed at the front end of the drive shaft 12. The screw hole 12a is formed at the end of the drive shaft 12 with a bolt (not shown) by a pulley 18 (not shown).
Is for fixing. The drive shaft 12 is drivingly connected to a vehicle engine E as an external drive source via a power transmission belt 19 wound around the pulley 18. Therefore, when the pulley 18 is rotated by the external drive source,
The drive shaft 12 and the first rotor 13 are also rotated together with the pulley 18.

The heat generation principle of the vehicle heat generator according to the present embodiment is based on the principle that the second rotor 16 actively rotates as the main shearing means, thereby shearing the viscous fluid in the heat generating chamber 5 to generate heat due to fluid friction. Is to produce In this case, the cylindrical outer peripheral surface of the second rotor 16 serves as a main shearing surface, and the viscous fluid interposed in the clearance h2 between the shearing surface and the inner peripheral surface of the stator 2 mainly causes the shearing action. Receiving fever. However, as described above, the second rotor 16 is not mechanically directly connected to the external drive source, but is indirectly connected to the first rotor 13 directly connected to the external drive source via the fluid clutch. It simply forms a connection. That is,
Depending on whether torque is transmitted from the first rotor 13 to the second rotor 16 via the fluid coupling medium, the second rotor 16 may or may not be forcibly rotated. In this sense, the greatest feature of the present embodiment resides in the selective power transmission from the first rotor 13 to the second rotor 16 via a fluid clutch.

First, in order to qualitatively understand the operation of the heat generator according to the present embodiment, an outline of selective torque transmission from the first rotor 13 to the second rotor 16 will be briefly described. Power from the vehicle engine E (external drive source) is transmitted to the power transmission belt 1
When the drive shaft 12 and the first rotor 13 are transmitted to the pulley 18 via the pulley 9, the drive shaft 12 and the first rotor 13 are rotated together with the pulley 18. When the first rotor 13 starts rotating, the second rotor 16 is in a stationary state and does not generate heat due to shearing. Therefore, the temperature of the viscous fluid is low, and therefore the viscosity thereof is high. Therefore, the coupling area 17
The viscous fluid staying in the medium exerts its function as a fluid coupling medium, through which the rotational torque of the first rotor 13 is transmitted to the second rotor 16, and the second rotor 16 rotates.
Accordingly, in the clearance h2 between the inner peripheral surface (that is, the stationary surface) of the stator 2 as the wall surface of the heating chamber and the outer peripheral surface (that is, the movable surface) of the second rotor 16, the viscous fluid moves relative to the opposing surfaces. Heat is generated by the shearing action based on the speed difference. The heat generated by the shearing is exchanged with the circulating water flowing through the water jacket 6 as the heat radiating chamber via the stator wall, and the heated circulating water is supplied to the heating of the vehicle interior through the heating circuit.

As the first rotor 13 and the second rotor 16 rotate, a viscous fluid flows in the heat generating chamber 5.
For this reason, the exchange and mixing of the viscous fluid easily occur between the coupling region 17 and the clearance h2 region between the inner peripheral surface of the stator 2 and the outer peripheral surface of the second rotor 16.

As the second rotor 16 rotates, the stator 2
The viscous fluid in the clearance h2 between the inner peripheral surface of the second rotor 16 and the outer peripheral surface of the second rotor 16 gradually decreases its viscosity together with the heat generation. This high-temperature low-viscosity viscous fluid also replaces or mixes with the low-temperature high-viscosity viscous fluid in the coupling region 17 as described above. That is, both rotors 1
With the rotation of 3, 16 the temperature distribution and the viscosity distribution of the viscous fluid in the heat generating chamber 5 are made uniform. This is limited to the local area of the coupling area 17,
This means that high-temperature, low-viscosity viscous fluids (fluid coupling media) will be improved.

The lowering of the viscosity of the viscous fluid in the coupling region 17 means that the viscous fluid gradually reduces its function as a fluid coupling medium for transmitting a rotational torque from the first rotor 13 to the second rotor 16. I do. Thus, when the torque transmission from the first rotor 13 to the second rotor 16 via the fluid coupling medium weakens, the rotation speed of the second rotor 16 decreases, and the shearing force decreases. Then, heat generation in the clearance between the inner peripheral surface of the stator 2 and the outer peripheral surface of the second rotor 16 is gradually suppressed, and the temperature rise of the viscous fluid in the heat generating chamber 5 is stopped.

At the time of steady rotation of the pulley 18 and the first rotor 13, the torque transmission action from the first rotor 13 to the second rotor 16 and the shear heat generation action by the second rotor 16 are delicately balanced to generate the heat generation. The vessel exhibits a stable heat generation capability. However, when the rotation speed of the vehicle engine E becomes higher than usual and the rotation of the second rotor 16 together with the first rotor 13 becomes excessively high, the fluid clutch operates due to the decrease in the viscosity of the viscous fluid as described above. Thus, the rotational force of the second rotor 16 is weakened, and the shear heat generation capability is suppressed autonomously.

On the other hand, when the shear heat generation effect of the second rotor 16 is suppressed and the temperature of the viscous fluid tends to decrease, the torque transmission operation from the first rotor 13 to the second rotor 16 increases again, and the heat generation amount decreases. Is stopped. This is because the temperature drop of the viscous fluid is not
This is for increasing the viscosity of the viscous fluid and regaining its function as a fluid coupling medium. As described above, even when the vehicle engine E as the external drive source falls into an unsteady state, the heat generator of the present embodiment autonomously adjusts the shear heat generation capability.

Next, from the first rotor 13 to the second rotor 16
Quantitative consideration will be given to the transmission of torque to the motor and the amount of heat generated by shearing of the second rotor 16. Here, the viscosity coefficient of the viscous fluid (silicone oil) is μ, the angular velocity of the first rotor 13 is ω1, the angular velocity of the second rotor 16 is ω2, and the circular constant is π. The radius r1, the radius r2, the interval h1, the clearance h2, the total length L1, and the total length L2 are as described above.

The transmission torque Tt from the first rotor 13 to the second rotor 16 is represented by the following equation (1).

[0045]

(Equation 1) On the other hand, the torque required when the second rotor 16 rotates at the angular velocity ω2 in the heat generating chamber 5, that is, the torque Th that contributes to heat generation is expressed by Expression 2.

[0046]

(Equation 2) When the second rotor 16 is the main shear heat generating means, the theoretical heat value Q of this heat generator is expressed as in Equation 3.

[0047]

(Equation 3) By the way, since all the power is supplied to the second rotor 16 from the first rotor 13, the transmission torque Tt and the heat generation contribution torque Th should be equal. When the equation of Tt = Th is expanded and arranged, a relationship as shown in Expression 4 is established between the angular velocities ω1 and ω2.

[0048]

(Equation 4) As can be seen from Expression 4, the angular velocity ω2 of the second rotor 16
Is always smaller than the angular velocity ω1. Equation 4 does not include the viscosity coefficient μ, and h in Equation 4
1, h2, r1, r2, and L2 are all geometrical dimensions of the heat generator and can be uniquely determined. Therefore, when the angular velocity ω1 of the first rotor 13 is determined, the angular velocity ω2 of the second rotor 16 is also uniquely determined.

The transmission torque Tt shown in the equation 1 is a function of the angular velocity difference (ω1−ω2).
Is shown. Therefore, by substituting Equation 4 into Equation 1, ω2 can be eliminated from Equation 1. In this case, it is clear that the equation of the transmission torque Tt can be summarized into a functional form of Tt = μ × f (ω1). Although the detailed formula of f (ω1) is not shown, it is certain that only the angular velocity ω1 is a variable function.
Note that the viscosity coefficient μ is a function of temperature.

The equation of Tt = μ × f (ω1) suggests that if the angular velocity ω1 is constant, if the viscous fluid becomes high temperature and the viscosity coefficient μ decreases, the first rotor 13 The point is that the transmission torque Tt to the two rotors 16 also decreases. If the transmission torque Tt becomes smaller, the theoretical heating value Q also tends to be suppressed according to Equation 3. On the other hand, when the temperature of the viscous fluid decreases and the viscosity coefficient μ increases, the transmission torque Tt also increases and the theoretical calorific value Q tends to increase. The results of this quantitative consideration are consistent with the qualitative effects described above.

The effects of the first embodiment are enumerated below. ○ Opposite surface 13 between first rotor 13 and second rotor 16
The silicone oil (viscous fluid) in the coupling area 17 between a and 16a functions as a fluid coupling medium, and the fluid coupling medium and the two rotors 13 and 16 constitute a fluid clutch. As described above, the fluid clutch selectively adjusts the torque transmission from the first rotor 13 to the second rotor 16 according to the temperature of the viscous fluid in the heat generating chamber 5. As described above, the driving force (or rotation speed) of the second rotor 16 as the main shearing means can be optimized by the autonomous torque transmission adjusting operation of the fluid clutch built in the heat generating chamber 5. In other words, even when the driving force of the external driving source transmitted by the first rotor 13 fluctuates, the heat generator of the present embodiment can self-adjust the heat generation amount without being influenced by the fluctuation. .

In the present embodiment, the torque transmission adjustment to the second rotor 16 can be achieved with the extremely simple structure of the fluid clutch as described above, and a special power transmission adjustment is provided outside the heat generator. No additional mechanism (eg, electromagnetic clutch) is required. For this reason, the heat generator of the present embodiment cannot be a factor that causes an increase in the size and complexity of the heating system for a vehicle, and has excellent suitability as a heat generator for a vehicle.

Since the amount of heat generated by the second rotor 16 can be self-adjusted based on the temperature of the viscous fluid, the viscous fluid does not exceed its heat resistance limit and does not enter an overheated state. Therefore, deterioration of the viscous fluid due to overheating can be prevented beforehand, and necessary heat generation performance can be maintained for a long time.

In the water jacket 6, a flow path P extending from the entrance communication hole 9 to the exit communication hole 10 is formed by a plurality of ridges 7, and a plurality of ridges 7 are provided on the inner wall surface of the flow path P. Grooves 8 are formed. The circulating water moving along the flow path P flows around the heat generating chamber 5 while being guided by the ridges 7 constituting the flow path. And
With this flow path P, the contact time between the circulating water and the stator 2 as the heat transfer member can be kept constant and long, and the contact area can be enlarged by forming the groove 8. Therefore, heat exchange from the heat generating chamber 5 to the water jacket (radiation chamber) 6 can be performed stably and efficiently.

(Second Embodiment) FIG. 5 shows a vehicle heat generator according to a second embodiment. This vehicle heat generator includes housings 1, 2, 3, 4, a water jacket (radiation chamber) 6,
As far as the pulley 18 is concerned, the configuration is the same as that of the first embodiment, and the configuration of the contents contained in the heating chamber 5 is different.
In particular, the configuration of the first rotor 13, the second rotor 16, and the portion related to the fluid coupling medium therebetween is different. Therefore,
This difference will be mainly described.

According to the heat generator of the second embodiment, as shown in FIG. 5, the drive shaft 12 is rotatably supported by the front and rear housings 3, 4 via bearings 19, 20. I have. These bearings 19 and 20 are bearing devices with seals, and seal the front and back of the heat generating chamber 5 respectively. Therefore, the heat generating chamber 5 is provided as a liquid-tight internal space in the housing.

The drive shaft 12 extends so as to penetrate the heating chamber 5 back and forth. A first rotor 13 is fixed to substantially the center of the drive shaft 12, and the first rotor 13 rotates integrally with the drive shaft 12. The first rotor 13 has a cylindrical or cylindrical shape. In the heating chamber 5,
A second rotor 16 is housed in addition to the first rotor 13. The second rotor 16 is provided so as to cover the first rotor 13 and the drive shaft 12. This second rotor 1
Reference numeral 6 denotes a cylindrical or columnar shape. Bearings 21 and 22 are provided on the inner peripheral portion at the front end and the inner peripheral portion at the rear end of the second rotor 16.
The second rotor 16 is coaxial with the drive shaft 12 by the two bearings 21 and 22.
And are rotatably supported.

A predetermined space is secured between the outer peripheral surface of the first rotor 13 and the outer peripheral surface of the drive shaft 12 which are opposite surfaces, and the inner peripheral surface of the second rotor 16. The ring area 17 is formed. On the other hand, a predetermined clearance is secured between the outer peripheral surface of the second rotor 16 and the inner peripheral surface of the stator 2. As in the first embodiment, a predetermined amount of silicone oil (a viscous fluid) is filled in the heat generating chamber 5. This viscous fluid can reach almost all clearances in the heating chamber 5. The viscous fluid that has spread to the coupling area 17 functions as a fluid coupling medium. As in the first embodiment, the fluid coupling medium in the coupling area 17 includes the first and second rotors 13 and 1.
6 together with a "fluid clutch".

The heat generator of the second embodiment operates similarly to the heat generator of the first embodiment. That is, the torque transmission adjustment from the first rotor 13 and the drive shaft 12 to the second rotor 16 is autonomously performed by the fluid clutch. Therefore, also in the second embodiment, the same effect as in the first embodiment can be obtained. In addition, the drive shaft 12 (the first rotor 1
3) and the second rotor 16 are supported at two points by respective bearing devices at predetermined intervals in both the front and rear directions.
There is an advantage that a predetermined interval of the coupling area 17 provided between the third and drive shafts 12 and the second rotor 16 can be kept constant.

(Modification) The first and second embodiments can be modified and embodied as follows. In the coupling area 17 formed between the first rotor 13 and the second rotor 16, means for increasing torque transmission may be provided. For example, in order to form a labyrinth groove that matches between the first rotor 13 and the second rotor 16,
Each of the opposing portions of the rotors 13 and 16 is formed with an uneven stripe,
The labyrinth-like coupling area 17 is ensured between the opposed parts by the close arrangement of the two. That is, in the case of the first embodiment, the drive shaft 1 is provided on the rear end face 13a of the first rotor 13 and the front end face 16a of the second rotor 16.
The concavo-convex strip is formed so as to extend in a concentric arc shape about the axis 2. In the case of the second embodiment, the drive shaft 1 is provided on the outer peripheral surface of the first rotor 13 and the inner peripheral surface of the second rotor 16.
The uneven strip is formed so as to extend in the circumferential direction of No. 2. With such a configuration, the same effects as those of the first and second embodiments can be obtained, and in addition, the effect of transmitting torque from the first rotor 13 to the second rotor 16 via the fluid coupling medium is enhanced. As a result, the heat generation capability in the clearance between the second rotor 16 and the stator 2 can be further improved.

In the first embodiment, the first rotor 13
Has a disk shape, and functions only as a torque supply side member of the fluid clutch.
The rotor 16 may have a cylindrical shape, and the cylindrical outer peripheral surface may serve as a shearing surface.

(Definition of Terms) As used herein, the term "viscous fluid" means any medium that generates heat based on fluid friction under the shearing action of a cylindrical or disk-shaped rotor. Not limited to high viscosity liquids and semi-liquids,
Furthermore, it is not limited to silicone oil.

[0063]

As described in detail above, according to the vehicle heat generator described in each claim, it is possible to autonomously adjust the heat generation amount without using an external mechanism, and as a result, There is an effect that the heat generation performance as required can be continuously exhibited while preventing deterioration due to overheating of the fluid.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a vehicle heat generator according to a first embodiment.

FIG. 2 is a developed view of a stator constituting the vehicle heat generator shown in FIG.

FIG. 3 is a cross-sectional view taken along line AA of FIG.

FIG. 4 is an explanatory view showing dimensions and the like of each part of the vehicle heat generator shown in FIG. 1;

FIG. 5 is a longitudinal sectional view of a vehicle heat generator according to a second embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Central housing, 2 ... Stator, 3, 4 ... Front side and rear side housings (1, 2, 3, 4 constitute the housing of a heat generator), 5 ... Heat generation chamber, 6 ... Water jacket 12) drive shaft, 13 ... first rotor, 13a ... end face, 16 ... second rotor (constituting shearing means), 16a ... end face, 17 ... coupling area, 18 ...
Pulley, 19: power transmission belt, C: rotation axis, h1,
h2: clearance, P: distribution route in the heat radiation chamber.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Hidefumi Mori 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (72) Inventor Takanori Okabe 2-1-1, Toyota-cho, Kariya-shi, Aichi Share Inside Toyota Industries Corporation (72) Inventor Nobuaki Hoshino 2-1-1 Toyota-cho, Kariya City, Aichi Prefecture Co., Ltd. Inside Toyota Industries Corporation (72) Inventor Kazuhiko Minami 2-1-1 Toyota-machi, Kariya City, Aichi Prefecture Shares Inside Toyota Industries Corporation

Claims (5)

[Claims] 1. A housing, a drive shaft rotatably provided in the housing, a heat generating chamber and a heat radiating chamber defined in the housing, and disposed in the heat generating chamber via the drive shaft. A shearing means driven based on the power supply of the vehicle, generating heat by shearing the viscous fluid in the heat generating chamber by the shearing means, and exchanging the heat with a circulating fluid flowing through the heat radiating chamber. A heat generator, wherein a first rotor rotatably provided in the heat generating chamber and operatively connected to the drive shaft, and the drive shaft and the first rotor are not mechanically connected to each other. A second rotor as the shearing means rotatably provided in the heat generating chamber, wherein the first rotor and the second rotor constitute a fluid clutch together with a viscous fluid interposed between the two rotors. That Heat generator for a vehicle according to symptoms. 2. The first rotor and the second rotor each have opposing surfaces, and the opposing surfaces are separated from each other by a predetermined distance in the heat generating chamber, and a viscous fluid is interposed between the opposing surfaces. The heat generator for a vehicle according to claim 1, wherein a coupling region is formed. 3. The second rotor has a cylindrical shape, and a predetermined clearance is provided between an outer peripheral surface of the cylindrical second rotor and an outer peripheral surface of the heat generating chamber facing the outer peripheral surface. The heat generator for a vehicle according to claim 1, wherein the heat generator is provided. 4. The heat generator for a vehicle according to claim 3, wherein the heat radiation chamber is provided so as to surround the predetermined clearance along an outer peripheral surface of the second rotor. 5. A pulley is provided at an end of the drive shaft, and the drive shaft and the first rotor are directly driven by an external drive source via a power transmission belt wound around the pulley. 5. The method according to claim 1, wherein
The vehicle heat generator according to any one of claims 1 to 4.