JPH11227452A - Variable capacity heat generator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable capacity heat generator excellent in a variable control property for heating capacity even using high-viscous fluid, and easy in miniaturization. SOLUTION: A drive shaft 10 and a rotor 20 are rotatably housed in a heating chamber 4 demarcated in housings 1 and 2, and viscous fluid (e.g. silicone oil) is put in the clearances between the inner wall surface of the chamber 4 and the outer surface of the rotor 20. An outer peripheral member 23, one of constitution elements of the rotor 20, is composed of elastically deformable raw material. A pressure governing chamber 24 is demarcated in the rotor 20, and is connected to inner-pressure adjusting mechanisms 25, 26, 27, 28, and 41 via a passage 14 in the shaft 10. The clearances are increased/decreased based on the elastic deformation of the members 23 in accordance with the inner pressure change in the chamber 24, to variably control the heating capacity of a heat generator.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has a heat generating chamber and a heat radiating chamber partitioned in a housing, and shears a viscous fluid contained in the heat generating chamber by a rotor rotatably provided in the heat generating chamber. It is a heat generator that generates heat by heat exchange of the heat with a circulating fluid flowing through the radiating chamber,
The present invention relates to a variable-capacity heat generator capable of autonomously or variably adjusting the heat generation capacity.

[0002]

BACKGROUND OF THE INVENTION Published German Patent Application No. 383.
No. 2966 (DE 383 published on April 5, 1990)
2966A1) discloses a heating assembly as a heat generator incorporated in a vehicle heating system. Hereinafter, FIG. The outline of the heating assembly will be described with reference to FIG.

A work space 48 (corresponding to a heating chamber) and a work space 4 are provided in the housing of the heating assembly.
8 and a ring space 62 (corresponding to a water jacket) surrounding the inner space 8. Further, in the housing,
A storage space 58 adjacent to the front of the work space 48 is defined. The storage space 58 and the working space 48 are separated from each other by an intermediate wall 60. The intermediate wall 60 is formed with a fluid supply port 66 connecting the working space 48 and the storage space 58 and a coupling passage 68 for fluid recovery. ing. The passage 66 is a passage opened and closed by a lever 72. The lever 72 is urged by a coil spring 73 in a direction to open the opening 66, and is urged by a bimetal leaf spring 76 in a direction to close the opening 66. That is, the entrance 6
6 is determined by the balance between the urging forces of the springs 73 and 76.

A drive shaft 52 is rotatably supported at the rear of the housing. A wheel 50 (corresponding to a rotor) is provided at one end of the drive shaft 52 so as to be integrally rotatable in the work space 48, and a belt pulley 44 is fixed to the other end of the drive shaft 52. The belt pulley 44 is operatively connected to the vehicle engine via a belt. A required amount of viscous fluid 78 is contained in the working space 48 and the storage space 58 so as to reach the gap between the outer wall of the wheel 50 and the inner wall of the working space 48. When the driving force of the engine is transmitted to the drive shaft 52 of the heating assembly, the wheels 50 rotate in the work space 48, and the viscous fluid interposed between the outer wall of the wheel and the inner wall of the work space is sheared to be fluid. Generates heat based on friction. The heat generated in the working space 48 is transmitted to a cooling medium (engine cooling water) flowing in the ring space 62 via a partition of the housing. The heated cooling medium is supplied to a heat exchanger of a heating device for a vehicle and is used for heating a vehicle interior.

In this heating assembly, two springs 7
Based on the opening / closing control of the opening 66 by the lever 72 whose position is controlled by the members 3 and 76, the heat generation capability is adjusted in a feedback manner. That is, when the high-temperature viscous fluid is recovered from the work space 48 to the storage space 58 via the coupling passage 68, the bimetal leaf spring 76 responds to the rise in the environmental temperature.
Of the coil spring 73 and the lever 7
Reference numeral 2 is disposed at a position where the opening 66 is closed. Then, the re-supply of the viscous fluid from the storage space 58 to the work space 48 is stopped, so that the amount of the viscous fluid in the work space 48 gradually decreases, and the calorific value based on the fluid friction decreases. As a result, when the temperature of the viscous fluid recovered from the working space 48 to the storage space 58 shows a tendency to decrease, the bimetal leaf spring 76
Of the coil spring 73 is weakened,
The lever 72 moves in a direction to open the passage 66. Then
The supply of the viscous fluid from the storage space 58 to the work space 48 is restarted, and the amount of the viscous fluid in the work space 48 is increased to increase the heat generation.

[0006]

In a heat generator intended to generate heat by shearing a viscous fluid as described above, it has been confirmed that the viscosity of the viscous fluid used has a great influence on the heat generation capacity. That is, the use of a viscous fluid having a high viscosity tends to increase the heat generation efficiency and increase the heat generation amount.

However, as the viscosity of the viscous fluid increases, it becomes more difficult for the viscous fluid to circulate (move) in the housing. In the prior art heating assembly, the viscous fluid is provided with a working space 48 and a storage space 58.
By adjusting the amount of the viscous fluid in the work space 48 while circulating between them, feedback control of the calorific value is realized. Therefore, when designing a heat generator that adopts the principle of variable capacity such as the above-mentioned heating assembly, it is necessary to properly balance the mobility of the viscous fluid in the housing and the required amount of heat generation. A viscous fluid of viscosity must be selected. However, even in such a case, if the viscosity of the viscous fluid is set to be high in consideration of the heat generation efficiency, the fluidity of the viscous fluid in the housing may be reduced, and the responsiveness of the feedback control may be deteriorated. On the other hand, if the viscosity of the viscous fluid is set to a low value with emphasis on the responsiveness of the feedback control, it will be necessary to increase the size of the shearing means such as the rotor and increase the amount of use of the viscous fluid in order to secure the absolute heat generation. . In any case, from the viewpoint of the viscosity of the viscous fluid, the two requirements (improvement of the responsiveness of feedback control and securing of the calorific value) are inconsistent, and setting the viscosity of the viscous fluid is very difficult.

[0008] A main object of the present invention is to provide a variable-capacity heat generator which is excellent in variable control of the heat generation capacity while adopting a design having high shear heat generation efficiency. A further object of the present invention is to provide a small-capacity variable heat generator which is excellent in variable control of the heat generation capacity even when a high-viscosity viscous fluid is used and which can be easily miniaturized.

[0009]

According to a first aspect of the present invention, there is provided a heat generating chamber and a heat radiating chamber partitioned in a housing, and a viscous fluid contained in the heat generating chamber is rotatably provided in the heat generating chamber. A heat generator that generates heat by shearing with the rotor, and exchanges the heat with a circulating fluid flowing through the heat radiating chamber, wherein the rotor forms a clearance between the rotor and an inner wall surface of the heat generating chamber. The rotor component that has a shearing surface to provide the shearing surface and is elastically deformable in a direction to change the clearance is a variable capacity heat generator.

A viscous fluid stays in the clearance between the inner wall surface of the heat generating chamber of the heat generator and the shearing surface of the rotor. The viscous fluid in the clearance region generates heat based on fluid friction due to the shearing action of the shearing face of the rotating rotor. The shear calorific value tends to increase as the clearance decreases, and to decrease as the clearance increases. According to the invention, the rotor component providing the shearing surface is elastically deformable in the direction of changing said clearance. Therefore, by appropriately stimulating the rotor components from inside or outside the heat generator to elastically deform the rotor components, it is possible to appropriately change the clearance between the wall surface of the heat generating chamber and the shearing action surface. Variable adjustment of shear heat generation capability is possible. According to the principle of the variable adjustment of the heat generation capacity, it is not necessary to move the viscous fluid from the heat generation chamber to another chamber in the housing, and the variable adjustment of the shear heat generation capacity can be achieved simply by elastically deforming the rotor component in a specific direction. Achieved. Therefore, the variable controllability of the heat generation capability is dramatically improved.

The stimulus that causes the rotor components to elastically deform includes thermal expansion of the viscous fluid itself staying in the clearance area and changes in the internal fluid pressure when a fluid area is provided inside the rotor. can give.

According to a second aspect of the present invention, in the variable-capacity heat generator according to the first aspect, the rotor includes a pressure regulating chamber therein, and the rotor component for providing the shearing action surface includes: It is characterized by being elastically deformed in response to a change in the internal pressure of the pressure regulating chamber.

[0013] According to this configuration, the pressure regulating chamber as a fluid region is set inside the rotor. By appropriately changing the internal pressure of the pressure regulation chamber, it becomes possible to control the elastic deformation of the rotor components, that is, to control the clearance between the wall surface of the heating chamber and the rotor shearing surface. As Pascal's principle suggests, changes in fluid pressure are immediately propagated throughout the fluid region. Therefore, the responsiveness of the clearance control based on the internal pressure control of the pressure regulation chamber is extremely excellent.

According to a third aspect of the present invention, in the variable capacity heat generator according to the second aspect, the rotor is provided on a drive shaft rotatably supported in the housing. The pressure chamber is connected to an internal pressure adjusting mechanism provided outside the housing via a passage provided in the drive shaft.

According to this configuration, the internal pressure of the pressure regulating chamber is adjusted by the internal pressure adjusting mechanism provided outside the housing. Since the communication between the pressure regulation chamber and the internal pressure adjusting mechanism is ensured by the passage provided in the drive shaft, the structure of the heat generator can be prevented from becoming complicated as much as possible. Further, since the internal pressure of the pressure regulation chamber is controlled by an internal pressure adjusting mechanism provided outside the housing, fine feedback control using a microcomputer can be easily realized.

According to a fourth aspect of the present invention, in the variable capacity heat generator according to any one of the first to third aspects, the rotor has a drum shape, and an outer peripheral portion of the drum-shaped rotor has the outer periphery. It is characterized by being formed by an elastically deformable rotor component.

According to this configuration, the outer peripheral surface of the drum-shaped rotor serves as the shearing surface. Further, since the rotor has a drum shape, it is easy to provide the pressure regulating chamber in the rotor.

According to a fifth aspect of the present invention, in the variable-capacity heat generator according to any one of the first to third aspects, the rotor has a drum shape, and an end surface of the drum-shaped rotor has the end face. It is characterized by being formed by an elastically deformable rotor component.

According to this configuration, the end face of the drum-shaped rotor serves as the shearing action surface. Further, since the rotor has a drum shape, it is easy to provide the pressure regulating chamber in the rotor.

According to a sixth aspect of the present invention, in the variable capacity heat generator according to any one of the first to fifth aspects, at least a part of the elastically deformable rotor component is a heat-resistant rubber sheet. It is characterized by being formed.

The heat-resistant rubber sheet has both heat resistance and elasticity required as a material constituting the rotor of the heat generator, and is easily obtained and processed.

[0022]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) A variable-capacity heat generator for a vehicle as an auxiliary heat source of a vehicle heating device according to a first embodiment of the present invention will be described with reference to FIGS. explain.

As shown in FIG. 1, the housing of the vehicle heat generator according to the present embodiment comprises a front housing 1 and a rear housing 2. The front and rear housings 1 and 2 as housing components are made of an aluminum alloy. The front housing 1 has a main body 1a, a flange 1b formed on the outer periphery of the main body 1a, and an annular tubular portion 1c extending rearward from the main body 1a. On the other hand, the rear housing 2
Has a main body 2a and a bowl-shaped tubular portion 2b projecting forward from the main body 2a. Front housing 1
And the rear housing 2 include an annular tubular portion 1 in a bowl-shaped tubular portion 2b.
c are housed together while accommodating them, and fastened together by a plurality of bolts 3 (see FIG. 2).

As a result of the mutual connection of the front and rear housings 1 and 2, a heat generating chamber 4 is formed in a region surrounded by the main body 1a of the front housing 1, the annular cylindrical portion 1c, and the main body 2a of the rear housing 2. Is done. In a region surrounded by the flange portion 1b of the front housing 1, the annular tubular portion 1c, and the bowl-shaped tubular portion 2b of the rear housing 2, a water jacket 5 as a heat radiating chamber is formed.

As shown in FIGS. 1 and 2, a water inlet port 6 and a water outlet port 7 are provided side by side on the outer peripheral portion of the bowl-shaped tubular portion 2b of the rear housing 2. The circulating fluid (for example, engine cooling water) is supplied to the engine 3 constituting the vehicle heating system.
1. Circulating between the heat generator and the heating circuit 32 (including a heater core not shown). Then, the water inlet port 6 takes the circulating fluid from the engine 31 into the water jacket 5. The water outlet port 7 sends out the circulating fluid that has made a round in the water jacket 5 to the heating circuit 32. As shown in FIG. 1 and FIG.
A plurality of ribs 5a (two in the present embodiment) projecting in the circumferential direction protrude from the annular cylindrical portion 1c. These ribs 5a serve as guide walls for guiding the flow of the circulating fluid in the water jacket 5, and set the flow path of the circulating fluid in the heat radiation chamber.

The front and rear housings 1, 2
A drive shaft 10 is rotatably supported via bearings 8 and 9. Each of the bearings 8 and 9 is a bearing device with a seal. The bearing 8 is interposed between the inner peripheral surface of the front housing main body 1a and the outer peripheral surface of the drive shaft 10, and seals the front of the heat generating chamber 4. The bearing 9 is interposed between the inner peripheral surface of the rear housing body 2a and the outer peripheral surface of the drive shaft 10, and seals the rear of the heat generating chamber 4.

A passage 11 is formed in the rear housing 2 to allow the heat generating chamber 4 to communicate with the outside of the housing. The passage 11 is closed by a drain bolt 12. Further, a rotor 20 is provided on the drive shaft 10 in the heat generating chamber 4 so as to be integrally rotatable. Heating room 4
As a result, the clearance region S is formed between the outer surface of the rotor 20 and the inner wall surface of the heat generating chamber 4. This clearance area is liquid-tight as long as the drain bolt 12 closes the passage 11.

As shown in FIGS. 1 and 3, the rotor 20
Is composed of a pair of metal fixed plates 21 and 22 and a cylindrical outer peripheral member 23. Each of the fixing plates 21 and 22 is a disk-shaped member having a radius R. The pair of fixed plates 21 and 22 are separated from each other by a predetermined distance L (L is a distance between the outer end surfaces of the fixed plates 21 and 22) in the heating chamber 4.
It is fixed on 0. The outer peripheral member 23 is provided between the fixed plates 21 and 22 so as to connect the outer peripheral edges of the fixed plates.
Is supported. The outer peripheral member 23 is formed of an elastically deformable material, for example, a heat-resistant rubber sheet.
Accordingly, the rotor 20 has a hollow drum shape having a radius R and a length L (where R <L) as a whole, and its internal space provides a pressure regulation chamber 24. The outer peripheral surface of the outer peripheral member 23 is a main shearing operation surface of the rotor 20. Therefore, the outer peripheral member 23 is an elastically deformable rotor component that provides a shearing surface.

As shown in FIG. 1, the drive shaft 10 has a first shaft extending at an axial position thereof.
It has a passage 13 and at least one second passage 14 formed to extend in a radial direction in a front end region of the first passage 13. The second passage 14 communicates the pressure regulation chamber 24 with the first passage 13. The tip of the pipe 25 is inserted into the second half of the first passage 13. This pipe 25
The drive shaft 10 and the drive shaft 10 are fitted so as to be relatively rotatable with each other.

A three-way valve 2 is provided at a branch point in the middle of the pipe 25.
6 are provided. The three-way valve 26 is connected to the pipe 25
Is a switching valve for selectively connecting to the vacuum pump 27 or the outside air. The three-way valve 26 is operatively connected to a forward / reverse rotatable motor 28, and changes its switching position in accordance with the operation of the motor 28. Therefore, in response to the operation of the motor 28, the pressure regulating chamber 24 becomes the first passage 13, the second passage 14,
It is connected to a vacuum pump 27 or outside air via a pipe 25 and a three-way valve 26.

The elastically deformable outer peripheral member 23
As shown in FIG. 1 and FIG. 3, when the internal pressure of the pressure regulation chamber 24 is about the atmospheric pressure, the pressure regulating chamber 24 is formed of a sheet-like material having elasticity and thickness enough to substantially maintain a cylindrical shape. On the other hand, when the inside of the pressure regulation chamber 24 is decompressed by the vacuum pump 27, the outer peripheral member 23 is recessed at a substantially central portion thereof toward the drive shaft 10, and changes from the cylindrical shape of FIG. 3 to that shown in FIG. Deforms into a slightly constricted shape. The pipe 25, the three-way valve 26, the vacuum pump 27, the motor 28, and a control device 41 described below constitute an internal pressure adjusting mechanism of the pressure regulation chamber 24.

In a clearance region S formed between the outer surface of the rotor 20 and the inner wall surface of the heat generating chamber 4, silicone oil as a viscous fluid (see FIG. Not shown in Figures 1 and 2, FIG.
4 is indicated by a satin pattern). The volume of the clearance region S is set to V1, and the drain bolt 12
When the volume of the passage 11 closed in the state is V2,
The filling amount of the silicone oil is determined so that the filling factor at normal temperature is in the range of 40% to 80% with respect to the sum of the volumes (V1 + V2). The reason why the filling rate of the silicone oil at normal temperature is not set to 100% in the first embodiment is in consideration of the thermal expansion of the silicone oil during heat generation.

Further, a bolt 1 is provided at the front end of the drive shaft 10.
5, the pulley 16 is fixed. This pulley 1
6 is operatively connected to an engine 31 as an external drive source via a power transmission belt 17 such as a V-belt. Therefore, the drive shaft 10 and the rotor 20 are rotated by the driving force of the engine 31 via the pulley 16. Along with this, the silicone oil staying in the clearance region S generates heat due to the shearing action of the rotor 20. This heat is transmitted to the circulating fluid flowing through the water jacket 5 via the annular tubular portion 1c, and the circulating fluid is reheated. Then, the circulating fluid sent from the water discharge port 7 to the heating circuit 32 is used for heating the vehicle interior and the like. The effect of varying the amount of heat generated by shearing the rotor 20 and the ability to generate heat will be described later in detail.

FIG. 1 schematically shows a control configuration of the heat generator of the present embodiment. This heat generator for a vehicle incorporates the control device 41 by itself or is connected to the control device 41 which is separated from the heat generator body. The control device 41 mainly performs variable control of the heat generation amount. When the control device 41 is provided separately from the vehicle heat generator body, an electronic control unit (ECU) of the engine 31 is provided.
May also have the function of the control device 41.

The control device 41 includes a CPU, a ROM, and a RAM.
And a control unit similar to a microcomputer having a built-in input / output interface (both not shown), and a control program stored in a ROM thereof in advance. The output side of the control device 41 is connected to the vacuum pump 27.
And the motor 28. The input side of the control device 41 is connected to a heater switch / temperature setting device 42, an ignition key switch 43, a rotation speed sensor 44, a room temperature sensor 45, and a water temperature sensor 46.

The heater switch / temperature setting device 42 is incorporated in an operation panel provided in the passenger compartment, and the occupant instructs operation and stop (ON / OFF) of the heating device.
Further, it is an input means for setting a desired vehicle interior temperature. The ignition key switch 43 is a switch for driving a starter motor (not shown) to start the stopped engine 31.

The rotation speed sensor 44 detects the rotation speed (rotation speed) of the crankshaft of the engine 31 or the rotation speed (rotation speed) of the drive shaft 10 (or pulley 16) that rotates integrally with the rotor 20. It is a number detecting means. The room temperature sensor 45 is a temperature detecting means for detecting the temperature in the vehicle compartment. The water temperature sensor 46 is temperature detection means for detecting the temperature of engine cooling water as a circulating fluid flowing through the heating circuit 32. The water temperature sensor 46 may be provided in the heating circuit 32, in the cylinder block of the engine 31, or in the water jacket 5 of the heat generator.

Next, the operation of the heat generator of the first embodiment will be described for each scene. (Scene 1: When the engine is started) When the engine 31 is stopped, the pulley 16 and the rotor 20 are also stopped, and the heat generation chamber 4 is stopped.
The viscous fluid inside is gathered toward the bottom of the clearance area S. When the occupant turns on the ignition key switch 43 to start the engine 31, the control device 41 activates the vacuum pump 27, and controls the three-way valve 26 by the motor 28, and connects the pressure regulating chamber 24 and the vacuum pump 27 to each other. It is arranged at a first switching position for communication. Thus, the pressure control room 2
By setting the pressure of 4 to a reduced pressure, the inside of the outer peripheral member 23 is made to have a negative pressure, and the elastically deformable outer peripheral member 23 is deformed into the constricted shape shown in FIG. This is because the starting torque of the rotor 20 operatively connected to the engine 31 is reduced as much as possible to reduce the load on the starter motor.

This point will be further described.
Since the viscous fluid in the inside attempts to prevent the rotor 20 from starting due to its viscosity, the stopped rotor 20 is restrained by the viscous fluid. The constraint force F largely depends on the viscosity V (μ) of the viscous fluid, but the width h of the clearance region S between the outer surface of the rotor 20 and the inner wall surface of the heat generating chamber 4 where the viscous fluid is retained. Is also affected by That is, if the viscosity V (μ) of the viscous fluid is constant, the restraining force F tends to increase as the clearance h is smaller. Therefore, as shown in FIG. 4, if the clearance is increased from h to (h + Δx) at least partially by reducing the pressure in the pressure regulating chamber 24, the restraining force F can be reduced accordingly. . By intentionally increasing the clearance h in this manner, the load torque of the starter motor operatively connected to the heat generator via the power transmission belt 17 can be reduced, and the engine 31 and the rotor 20 can be smoothly started. Can be realized.

After the engine 31 is started, as long as the heater switch 42 is turned off, the reduced pressure state of the pressure regulation chamber 24 is maintained by the vacuum pump 27. In addition, since the rotor 20 is constantly rotated during the operation of the engine 31, the viscous fluid contained in the heat generating chamber 4 is collected by the centrifugal force in the clearance area S on the outer periphery of the outer peripheral member 23, and the rotor 2 is rotated.
0 (the region between the outer end surfaces of the fixed plates 21 and 22 and the wall surface of the heat generating chamber) and hardly stays near the drive shaft 10.

(Scene 2: Operation at Maximum Heating Capacity) When the heater switch 42 is turned on after the engine 31 is started,
The control device 41 is based on the set temperature of the temperature setting device 42, the detected rotation speed of the rotation speed sensor 44, the room temperature from the room temperature sensor 45, and the circulating fluid temperature from the water temperature sensor 46.
The suction capacity of the vacuum pump 27 and the motor 28 are controlled so that the room temperature is optimized.

Specifically, when the temperature of the circulating fluid is not sufficiently high (for example, when the temperature does not reach 80 ° C.), the control device 41 drives the motor 28 to
At the second switching position where the pressure regulating chamber 24 is opened to the atmosphere. Then, since the pressure regulation chamber 24 returns to the atmospheric pressure, the rotor 2
The zero outer peripheral member 23 restores the cylindrical shape as shown in FIG. 3, and a constant clearance h is secured in the entire outer peripheral area of the outer peripheral member 23. This clearance h is, for example, several tens to several hundreds of micrometers (μm). During the rotation of the rotor 20, the clearance region S having the width h is filled with a viscous fluid, and generates heat by being subjected to a shearing action by the outer peripheral surface of the rotor 20 (that is, the outer peripheral surface of the outer peripheral member 23).

According to the theoretical analysis of the shear heat generation state in FIG. 3, the heat generation amount ΔQ1 on the outer peripheral surface of the rotor in the minute section Δl (delta el) divided along the axial direction of the rotor 20 (full length L) is as follows. It is expressed as in the equation (1).

[0044]

(Equation 1) In the equation (1), π is a circular constant, μ is a viscosity coefficient of a viscous fluid, ω is an angular velocity of the rotor 20, and R is a radius of the rotor 20.

If the sum of .DELTA.Q1 in each minute section .DELTA.l is calculated over the entire length L of the rotor, it becomes the total heat generation Q1 on the outer peripheral surface of the rotor 20 shown in FIG. Also, ΣΔl =
L. Therefore, the total calorific value Q1 on the outer peripheral surface of the rotor is
It is expressed as the following equation (2).

[0046]

(Equation 2) As can be seen from the equation (2), the total heat generation amount Q1 tends to increase as the clearance h is smaller.

(Scene 3: Operation for suppressing heat generation capability) When the heater switch 42 is in the ON state, the following a), b), and c) are performed.
In either case, the controller 41 controls the suction capacity of the vacuum pump 27 and the motor 28 in order to appropriately suppress the heat generation capacity of the heat generator. a) When the rotation speed detected by the rotation speed sensor 44 exceeds a predetermined threshold rotation speed, b) When the room temperature exceeds the set temperature of the temperature setting device 42, c) When the temperature of the circulating fluid is a predetermined upper limit temperature (For example, 80 ° C)
If exceeded.

Specifically, when any one of the above conditions a), b) and c) is satisfied, the control device 41 operates the three-way valve 26 by the motor 28 to operate the three-way valve 26 with the pressure regulating chamber 24. It is arranged at a first switching position for communicating with the middle vacuum pump 27. Further, if necessary, the suction capacity of the vacuum pump 27 is variably adjusted. In this manner, the inside of the pressure regulation chamber 24 is brought into an appropriate reduced pressure state, and the outer peripheral member 23 is deformed into the constricted shape shown in FIG. Thus, the calorific value of the heat generator is made lower than the total calorific value Q1 shown in the equation (2).

This point will be analyzed according to the equation (1). Consider a heat generation amount ΔQ2 on the outer peripheral surface of the rotor in a minute section Δl divided along the axial direction of the rotor 20 (overall length L) shown in FIG. Assuming that the radius of the outer peripheral member 23 in the minute section Δl is smaller than the original radius R by Δx (0 <Δx), the clearance in the same minute section Δl is larger by Δx than the original clearance h. .
Under this condition, the heat generation amount ΔQ2 is expressed by the following equation (3).

[0050]

(Equation 3) ΔQ in each minute section Δl over the entire length L of the rotor
If the sum of 2 is obtained, it becomes the total heat generation amount Q2 on the outer peripheral surface of the constricted rotor 20 shown in FIG. However, Q2
= ΣΔQ2, Q2 <Q1 is apparent. This is because it is clear that ΔQ2 <ΔQ1 when comparing the expressions 1 and 3 for each minute section Δl.

As described above, by making the inside of the pressure regulating chamber 24 moderately decompressed and deforming the outer peripheral member 23 into the constricted shape shown in FIG. 4, the calorific value Q2 of the heat generator can be reduced at the maximum heating capacity. The heat value can be made smaller than Q1.

The radius or clearance displacement Δx
Can be set to an arbitrary value by controlling the internal pressure of the pressure regulation chamber 24, that is, by controlling the suction capacity of the vacuum pump 27. When the material of the outer peripheral member 23 is a heat-resistant rubber sheet, Δx can be set in the range of 200 μm to 1 mm.

(Scene 4: When the heating device is stopped) Engine 3
When the heater switch 42 is turned off during the driving of the control unit 1, the control device 41 places the three-way valve 26 in the first switching position for communicating the pressure regulating chamber 24 and the operating vacuum pump 27 by the motor 28. At the same time, the internal pressure control of the pressure regulation chamber 24 is stopped. Then, the heat generating capability of the heat generator is set (suppressed) to the minimum.

Also, ON / OFF of the heater switch 42
Ignition key switch 43 is OFF regardless of
Then, the control device 41 stops the operation of the vacuum pump 27 after the three-way valve 26 is arranged by the motor 28 at the second switching position where the pressure regulating chamber 24 is opened to the atmosphere. This is because when the vacuum pump 27 is stopped while the pressure regulating chamber 24 in a reduced pressure state and the vacuum pump 27 are connected, the lubricating oil used in the vacuum pump 27 flows back into the pressure regulating chamber 24 via the pipe 25. This is because there is a danger.

According to the first embodiment, the following effects can be obtained. (A) The radius R of the rotor 20 and the rotor clearance h can be changed simultaneously in response to the internal pressure control of the pressure regulation chamber 24, and the heat generation capability of the heat generator can be quickly increased by the simultaneous variable synergistic effect of R and h. Can be variably adjusted.

(B) According to the present embodiment, since the movement of the viscous fluid is not required for the variable adjustment of the heat generation capacity, the variable control of the heat generation capacity can be performed as compared with the prior art (for example, the heating assembly of DE38332966A1). Excellent responsiveness. Further, according to this embodiment, it is easy to use a high-viscosity silicone oil, and the degree of freedom in designing the heat generator is increased.

(C) When the engine 31 and the rotor 20 are started, the pressure regulation chamber 24 in the rotor is depressurized to increase the rotor clearance h as much as possible.
It is possible to smoothly start the engine 31 and the rotor 20.

(D) According to the present embodiment, the rotor 20 can be formed to have a length L which is longer than the radius R while securing a sufficient heat generation amount. And the degree of freedom in setting the ratio to the vehicle can be increased, and the mountability on a vehicle can be improved. In particular, since the overall shape of the heat generator housing shown in FIG. 1 is very similar to the shape of the hydraulic pump for power steering, the power steering pump is provided in the space previously reserved for the power steering pump in the engine room. This heat generator can be arranged in place of the heat generator.

(Second Embodiment) A variable-capacity heat generator for a vehicle as an auxiliary heat source of a vehicle heating device according to a second embodiment will be described with reference to FIGS.

In the first embodiment, the filling amount of the silicone oil as the viscous fluid is determined so that the filling factor at normal temperature is in the range of 40% to 80% with respect to the volume sum (V1 + V2). . On the other hand, in the second embodiment, while the mechanical configuration of the heat generator main body is almost the same as that of the first embodiment, the amount of silicone oil filled in the heat generating chamber 4 is reduced by the filling rate at normal temperature. Is the volume sum (V1
+ V2) to be 97% to 99%. Incidentally, V1 is a clearance area S around the rotor 20.
V2 is the volume of the passage 11 closed by the drain bolt 12.

As shown in FIG. 5, in the second embodiment, a pressure pump 33 is provided at one branch end of the pipe 25 in place of the vacuum pump 27 in the first embodiment. The pressure pump 33 operates according to a command from the control device 41 and positively pumps air into the pressure regulation chamber 24 via the pipe 25 and the three-way valve 26. It should be noted that this pumping capacity is controlled by the control device 41.
Can be variably adjusted by a control signal from the controller. In the second embodiment, the pipe 25, the three-way valve 26,
The motor 28, the pressure pump 33, and the control device 41 constitute an internal pressure adjusting mechanism of the pressure regulation chamber 24.

According to the second embodiment, the engine 31
The three-way valve 26 is disposed at the second switching position where the pressure regulating chamber 24 is opened to the atmosphere at the start of the rotor 20 and immediately after the start of the rotor 20, and the outer peripheral member 23 has a cylindrical shape as shown in FIG. keeping. In other words, the heat generator is designed such that the clearance between the outer peripheral surface and the inner wall surface of the heat generating chamber 4 is maintained at a constant minimum value h over the entire outer peripheral member 23 so as to exhibit the maximum heat generating capability in the normal state. Have been.
Therefore, this heat generator operates at the maximum heat generation capacity immediately after the start of the rotor 20, and the silicone oil filled in the clearance area S is rapidly heated by the shearing action of the rotor 20. Note that there is no essential difference between the state of FIG. 5 and the state of FIG. 3 regarding the amount of heat generated on the outer peripheral surface of the rotor, and even in the state of FIG.

The silicone oil expands as its temperature rises. Since the silicone oil almost completely fills the clearance area S and has no escape, the expansion of the silicone oil causes the outer peripheral member 23 made of a heat-resistant rubber sheet to undergo elastic deformation. That is, the outer peripheral member 23
Reduces the increase in the oil pressure in the clearance region S while receiving the volume expansion of the silicone oil and deforming into a constricted shape as shown in FIG. At this time, the rotor clearance in the outer peripheral region of the rotor 20 is h
To (h + Δx) (see FIG. 6), and concomitantly, the radius of the rotor 20 decreases from R to (R−Δx). Therefore, when the rotor 20 shifts from the state of FIG. 5 to the state of FIG. 6, the heat generation capability of the heat generator is autonomously suppressed. Since the state of FIG. 6 is equivalent to the state of FIG. 4, the equation of Equation 3 also applies to the state of FIG.

It should be noted in this second embodiment that the opening of the pressure regulating chamber 24 to the atmosphere without any switching control of the three-way valve 26 can reduce the degree of expansion of the silicone oil reflecting the oil temperature. The point is that the rotor clearance h and the rotor radius R naturally change accordingly, and the heat generation capability is suppressed autonomously.

However, if it is necessary to limit the autonomous suppression of the heat generation capability as described above, the control device 41
Performs control for intentionally restoring the rotor clearance and the rotor radius. As a specific example in which it is necessary to limit the autonomous suppression of the heat generation capability, the temperature of the circulating fluid flowing through the water jacket 5 and the heating circuit 32 is low, and is quickly increased to near its upper limit temperature (for example, 80 ° C.). Sometimes you want to. In this case, the control device 41
The pressure pump 33 is operated, and the three-way valve 26 is arranged by the motor 28 at the first switching position where the pressure regulating chamber 24 and the pressure pump 33 are communicated. Then, as shown in FIG. 7, air is positively pumped from the pressure pump 33 into the pressure control chamber 24 to make the pressure control chamber 24 pressurized (pressurized), and the internal pressure of the pressure control chamber 24 is expanded by the silicone oil. The outer peripheral member 23 is maintained in a substantially cylindrical shape against the pressure. As a result, the heat generator is prohibited from autonomously suppressing the heat generation capacity, and maintains the heat generation capacity at or near the maximum heat generation capacity.

It should be noted that as a result of the outer peripheral member 23 being elastically deformed from the state of FIG. 5 to the state of FIG. 6 by the expansion pressure of the silicone oil, the outer peripheral member 23 in the state of FIG. 6 attempts to return to the state of FIG. A spring-like restoring force (repulsive force) is stored. Since this spring-like restoring force acts on the outer peripheral member 23 itself, even if the expansion pressure of the silicone oil is high, the pressure regulating chamber 2
The state shown in FIG. 7 (the original cylindrical shape of the outer peripheral member 23) can be realized only by slightly increasing the internal pressure of FIG. That is,
In the state of FIG. 7, the expansion pressure P1 of the silicone oil in the clearance area S is balanced with the sum (P2 + P3) of the pressurized internal pressure P2 of the pressure regulating chamber 24 and the restoring force P3 per unit area of the spring restoring force. It is doing.

In the second embodiment, the effects (a), (b), and (d) can be obtained as in the first embodiment. (Third Embodiment) In the first and second embodiments, the rotor constituting the outer peripheral portion of the rotor 20 is made of a material that can be elastically deformed. However, the variable capacity heat generation for vehicles according to the third embodiment is performed. In the container, the rotor constituent elements constituting each end face portion of the rotor were made of an elastically deformable material.

As shown in FIG. 8, the rotor 50 provided on the drive shaft 10 includes a pair of fixed plates 51 and 52 fixed on the drive shaft 10 at a predetermined interval, and a cylindrical outer peripheral member 53. And The outer peripheral member 53 is supported by a plurality of spokes 54 extending radially from each of the fixing plates 51 and 52. These members 51, 52, 53,
Each of the members 54 is formed of a highly rigid metal. Then, in each end face region of the rotor 50, each fixed plate 5
1, 52 and a peripheral member 53 surrounding the diaphragms 55,
56 is stretched. These diaphragms 55, 56
Is made of an elastically deformable material (for example, a heat-resistant rubber sheet). Thus, the rotor 50 has a hollow drum shape having a radius R and a length L (where L <R), and the inside thereof constitutes a pressure regulation chamber 57. The diaphragms 55 and 5
The outer surface of 6 functions as a shearing surface. Therefore, each diaphragm 55, 56 is positioned as an elastically deformable rotor component that provides a shearing surface.

The pressure regulating chamber 57 is provided in the first passage 13 of the drive shaft 10.
And a second passage 14, a pipe 25, and a three-way valve 26 to connect to a vacuum pump 27 or the atmosphere. In a clearance area S formed between the outer surface of the rotor 20 and the inner wall surface of the heat generating chamber 4, a required amount of silicone oil (not shown in FIG. 8 and shown in a matte pattern in FIG. 9) as a viscous fluid is put. Can be The filling amount of this silicone oil is such that the filling factor at normal temperature is based on the volume sum (V1 + V2).
It is determined to be in the range of 90% to 95%.

The diaphragms 55 and 56 are
If the internal pressure of the pressure regulating chamber 57 is about the atmospheric pressure, the pressure regulating chamber 57 maintains a substantially flat state (a state of being stretched vertically in FIG. 8).
As shown in FIG. 9, when the pressure regulating chamber 57 is put in a decompressed state by the vacuum pump 27, the pressure regulating chamber 57 is made of a sheet-like material having elasticity and thickness such that it is deformed into a shape recessed into the rotor.

The method of controlling the heat generation capability in the third embodiment is almost the same as in the first embodiment. That is, when the operation at the maximum heat generation capacity is required, for example, when the temperature of the circulating fluid flowing through the water jacket 5 is not sufficiently high, the three-way valve 26 causes the pressure regulating chamber 57 to be released from the atmosphere by the control device 41. disposed in a second switching position for opening, the diaphragm 55 and 56 becomes a state of straight is stretched in Figure 8, the clearance of the rotor end face region is the minimum value h _e (see FIG. 9).

According to the theoretical analysis of the shear heat generation state shown in FIG. 8, the heat value Q3 at each end face of the rotor 50 is expressed by the following equation (4). As can be seen from the equation, the calorific value Q3 at the rotor end face is inversely proportional to the clearance h _e.

[0073]

(Equation 4) On the other hand, when the engine 31 or the rotor 50 is started, or when the operation of suppressing the heat generation capability is required, the three-way valve 26 is controlled by the control device 41 so that the pressure regulating chamber 57 and the vacuum pump 27 communicate with each other. Arranged at the switching position, the pressure adjustment chamber 57 is in a reduced pressure state. Then, each of the diaphragms 55 and 56
Deformed into a shape recessed into the rotor 50 as shown in FIG. 9, the clearance of the rotor end face region is expanded from h _e in (h _e + Δx). It is apparent from the numerical formula 4 calorific value Q3 at the rotor end face is reduced by the expansion of the clearance h _e.

Therefore, in the heat generator of the third embodiment, as in the first embodiment,
The effects (b), (c) and (d) can be obtained.
The embodiment of the present invention may be modified as follows. In the first to third embodiments, the power transmission configuration in which the rotor and the engine are directly operatively connected is adopted. However, the electromagnetic clutch is provided in the power transmission path between the rotor and the engine as an external drive source. A mechanism may be provided, and power transmission and cutoff may be appropriately performed based on ON / OFF control of the electromagnetic clutch.

In the first embodiment, the outer peripheral member 23 is made of a heat-resistant rubber sheet. However, the outer peripheral member 23 is appropriately depressed in accordance with the degree of decompression of the pressure regulation chamber 24 (Δx is sufficient if it is depressed about 1 mm at the maximum). Any material can be used as long as it can be restored to its original shape, and there is no problem even if it is a thin metal plate. The same applies to the second and third embodiments.

In the first to third embodiments, a rubber-like sheet having a two-layer structure in which synthetic rubber is coated with a fluororesin (for example, Teflon) may be used as the elastically deformable rotor component. In this case, since the fluororesin having excellent heat resistance and chemical resistance comes into contact with the viscous fluid, the inner synthetic rubber is protected by the fluororesin.

In the first to third embodiments, the pressure regulating chamber 2
Although the inside of the space 4, 57 is filled with air, it may be filled with liquid such as water. That is, the medium that controls the internal pressure of the rotors 20 and 50 may be either a gas or a liquid.

In this specification, the term “viscous fluid” refers to any medium that generates heat based on fluid friction under the shearing action of a rotor, and is limited to high-viscosity liquids and semi-fluids. Of course, it is not limited to silicone oil.

[0079]

As described in detail above, according to the heat generator for a vehicle according to the claims, a variable capacity type excellent in variable controllability of heat generation capacity while adopting a design having high shear heat generation efficiency. It can be a heat generator for vehicles.

In particular, since it is not necessary to move the viscous fluid in the housing for the variable control of the heat generation capacity, even when a high-viscosity viscous fluid is used, the variable controllability of the heat generation capacity is not impaired, and the compactness is small. Therefore, it is easy to secure a sufficient amount of generated heat even if it is formed.

[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 cross-sectional view taken along line AA of FIG.

FIG. 3 is an enlarged sectional view showing a part of the rotor and a heat generating chamber when a pressure adjusting chamber of the rotor is brought to an atmospheric pressure state.

FIG. 4 is an enlarged sectional view showing a part of the rotor and the heat generating chamber when the pressure adjusting chamber of the rotor is in a reduced pressure state.

FIG. 5 is an enlarged cross-sectional view showing a part of a rotor and a heat generating chamber of a vehicle heat generator according to a second embodiment.

FIG. 6 is a cross-sectional view corresponding to FIG. 5, showing a case where a viscous fluid thermally expands.

FIG. 7 is a sectional view corresponding to FIG. 5 when the pressure adjustment chamber of the rotor is in a pressurized state.

FIG. 8 is a longitudinal sectional view of a vehicle heat generator according to a third embodiment.

FIG. 9 is an enlarged cross-sectional view showing a part of the rotor and the heat generating chamber when the pressure adjusting chamber of the rotor is in a reduced pressure state.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Front housing, 2 ... Rear housing, 4 ... Heat generation room, 5 ... Water jacket (radiation room), 10 ... Drive shaft, 13 ... 1st passage, 14 ... 2nd passage, 20 ... Rotor,
23 ... outer peripheral member (elastically deformable rotor component providing a shearing surface), 24 ... pressure regulating chamber, 25 ... pipe, 26
... three-way valve, 27 ... vacuum pump, 28 ... motor, 33 ...
Pressure pump, 41 ... Control device (25, 26, 27, 2)
8, 33, 41 constitute an internal pressure adjusting mechanism); 50: rotor; 55, 56: diaphragm (elastically deformable rotor component providing a shearing surface); 57: pressure regulating chamber;
h _e ... clearance.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Tatsuya Hirose 2-1-1, Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation

Claims (6)

[Claims] 1. A heat generating chamber and a heat radiating chamber partitioned in a housing, and heat is generated by shearing a viscous fluid contained in the heat generating chamber by a rotor rotatably provided in the heat generating chamber. A heat generator that exchanges heat with a circulating fluid flowing through the heat radiation chamber, wherein the rotor has a shearing surface that forms a clearance between the rotor and an inner wall surface of the heat generation chamber; A variable capacity heat generator, wherein the rotor component providing the shearing surface is elastically deformable in a direction to change the clearance. 2. The rotor according to claim 1, wherein the rotor has a pressure regulating chamber therein, and the rotor component providing the shearing surface elastically deforms in response to a change in the internal pressure of the pressure regulating chamber. 2. The variable capacity heat generator according to 1. 3. The housing according to claim 1, wherein the rotor is provided on a drive shaft rotatably supported in the housing, and the pressure regulating chamber is connected to the housing via a passage provided in the drive shaft. 3. The variable capacity heat generator according to claim 2, wherein the heat generator is connected to an internal pressure adjusting mechanism provided outside. 4. The rotor has a drum shape,
The variable capacity heat generator according to any one of claims 1 to 3, wherein an outer peripheral portion of the drum-shaped rotor is formed by the elastically deformable rotor component. 5. The rotor according to claim 1, wherein the rotor has a drum shape.
The variable capacity heat generator according to any one of claims 1 to 3, wherein an end face portion of the drum-shaped rotor is formed by the elastically deformable rotor component. 6. The variable-capacity heat source according to claim 1, wherein at least a part of the elastically deformable rotor component is formed of a heat-resistant rubber sheet. Generator.