JPH10272917A - Reciprocation type viscous heater - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a viscous heater capable of minimizing dispersion of heating capacity caused by dispersion of machining precision. SOLUTION: A double ended piston 23 is stowed inside cylinder bores 12b, 13b formed in inner cylinders 12i, 13i composing cylinder blocks 12, 13 communicably with a chamber 18 where a swash plate 24 is stowed. The swash plate 24 is supported integrally rotatable at the middle of the drive shaft 20 and each piston 23 is moored to the swash plate 24 through a shoe 26. A water jacket 27 is formed between inner cylinders 12i, 13i and outer cylinders 12o, 13o. The piston 23 is reciprocated inside cylinders 12b, 13b by rotation of the swash plate 24 following the rotation of the drive shaft 20 and heat generated by fluid fraction of viscous fluid intervening between the circumferential surface of the piston 23 and the wall surface of the cylinder bores 12b, 13b is exchanged by the circulating water inside the water jacket 27.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention divides a heat generating chamber and a heat radiating chamber in a housing, and generates heat by fluid friction in a viscous fluid stored in the heat generating chamber by the action of a member moving in the heat generating chamber. The present invention relates to a viscous heater for exchanging the heat with a circulating fluid flowing through the radiating chamber.

[0002]

2. Description of the Related Art Viscous heaters that utilize the driving force of a vehicle engine have attracted attention as auxiliary heat sources for vehicles. For example, Japanese Patent Laying-Open No. 2-246823 discloses a viscous heater incorporated in a vehicle heating device.

In this viscous heater, a front housing and a rear housing are connected to each other in a state of being opposed to each other, and a heat generating chamber is formed inside the heater and a water jacket (heat radiating chamber) is formed outside the heat generating chamber. I have. A drive shaft is rotatably supported on the front housing via a bearing device, and a rotor is fixed to one end of the drive shaft so as to be integrally rotatable in a heating chamber. The front and rear outer wall portions of the rotor and the inner wall portion of the heat generating chamber opposed thereto constitute labyrinth grooves which are close to each other, and a viscous fluid (for example, silicone oil) is interposed in a gap between the wall surface of the heat generating chamber and the wall surface of the rotor. I have.

When the driving force of the engine is transmitted to the drive shaft, the rotor rotates together with the drive shaft in the heating chamber, and viscous fluid interposed between the wall of the heating chamber and the outer wall of the rotor is rotated by the rotor. Shears to generate heat based on fluid friction. The heat generated in the heat generating chamber is exchanged with circulating water flowing in the water jacket, and the heated circulating water is supplied to an external heating circuit to be used for heating the vehicle.

[0005]

In the above-mentioned conventional viscous heater, since it is necessary to form irregularities for forming a labyrinth groove on the front and rear outer wall portions of the rotor, the rotor body has a larger axis than a radius from its axis. It has a shape similar to a short disk. In such a rotor, the main shearing action surface is the surface of the uneven ridges on the front and rear outer wall portions of the rotor, and the circling speed (that is, the shearing speed) increases as the uneven ridges are located farther from the axis of the rotor body. Therefore, in order to increase the calorific value of the heater, it is necessary to increase the rotor diameter, that is, to increase the outer diameter of the heater body.

Further, in a disk-type viscous heater, the calorific value is theoretically proportional to the fourth power of the radius, and therefore, the variation in the capacity due to the variation of the radius, the filling rate of the oil, the difference in the location of the oil, and the like. Becomes larger. That is, variations in processing accuracy greatly affect the heating capacity of the viscous heater. As a result, if the heating capacity is increased, that is, if the radius is set to be large in anticipation of the variation, there is a problem that the viscous fluid is overheated due to heat generation and is likely to be deteriorated.

The present invention has been made in view of the above-mentioned conventional problems, and an object of the present invention is to provide a viscous heater capable of reducing variations in heating capacity due to variations in processing accuracy.

[0008]

According to the first aspect of the present invention, a viscous fluid is interposed between a heat generating chamber provided in a housing and a wall surface of the heat generating chamber. A reciprocating member arranged so as to be able to reciprocate with
There is provided a driving means for driving the reciprocating member, and a heat radiating chamber provided adjacent to the heat generating chamber and exchanging heat generated by the reciprocating motion of the reciprocating member with a circulating fluid.

In this viscous heater, the reciprocating member reciprocates by the action of the driving means with the viscous fluid interposed between the viscous heater and the wall surface of the heating chamber. Then, heat generated by the fluid friction of the viscous fluid due to the reciprocating motion of the reciprocating member is exchanged with the circulating fluid in the radiating chamber. The amount of heat generated by the reciprocating motion of the reciprocating member depends on the fluid frictional force. The fluid frictional force is proportional to the viscosity coefficient of the viscous fluid, the reciprocal of the gap between the wall of the heating chamber where the viscous fluid is interposed and the reciprocating member, and the surface area of the reciprocating member corresponding to the gap. Therefore,
Unlike the disk type, the heating power is not affected by the fourth power of the processing accuracy of one member, and the heating capacity does not vary greatly even if the processing accuracy varies.

According to a second aspect of the present invention, in the first aspect of the present invention, the driving means includes a driving shaft for transmitting a rotational force of an external driving source, and a shoe via a rotation of the driving shaft. A cam plate for transmitting reciprocating motion to the reciprocating member.

According to the present invention, when the drive shaft is rotated by the torque of the external drive source, the cam plate rotates integrally with the drive shaft. The rotation of the cam plate is converted to reciprocating motion of the reciprocating member via the shoe. Other functions are the same as those of the first aspect.

According to the third aspect of the present invention, the cam plate is a swash plate supported on the drive shaft so as to be tiltable, and is provided with swash plate angle changing means for changing the tilt angle of the swash plate. .

According to the present invention, when the drive shaft is rotated by the torque of the external drive source, the rotation is converted into reciprocating motion of the reciprocating member via the swash plate and the shoe. The stroke of the reciprocating motion of the reciprocating member changes depending on the angle between the swash plate and the drive shaft. The smaller the swash plate angle (the angle between the plane orthogonal to the drive shaft and the swash plate), the shorter the stroke.
The calorific value decreases. The swash plate angle is changed by the swash plate angle changing means, so that the amount of heat generated during high-speed rotation is prevented from becoming excessive, and the required amount of heat generated during low-speed rotation can be secured.

According to a fourth aspect of the present invention, in the third aspect of the present invention, the swash plate is fixed to a rotation support member rotatably supported by the drive shaft so as to be relatively non-rotatable via a hinge mechanism. The swash plate angle changing means is connected to a chamber in which the swash plate is housed, and is a pressure adjusting means for adjusting a pressure in the chamber.

In the present invention, the rotary support is rotated integrally with the drive shaft, and the swash plate is rotated integrally with the rotary body via the hinge mechanism. The swash plate angle is changed by the pressure in the room in which the swash plate is housed. When the rotation speed of the drive shaft is the same, when the indoor pressure decreases, the swash plate angle increases and the amount of generated heat increases, and when the pressure increases, the swash plate angle decreases and the amount of generated heat decreases. The pressure in the room is adjusted to a desired value by the pressure adjusting means.

According to a fifth aspect of the present invention, in the third or fourth aspect of the present invention, the swash plate angle changing means increases the angle between the swash plate and the drive shaft at the time of startup. Adjust the angle.

In the present invention, the swash plate is started with a small angle, so that the torque required to drive the drive shaft at the time of starting is reduced. In the invention described in claim 6, in the invention described in any one of claims 2 to 5, machine oil is used as the viscous fluid.

In the present invention, since the lubricating property of the viscous fluid is good, the lubrication of the sliding portion such as between the cam plate or the swash plate and the shoe is improved, and the reliability and durability of the sliding portion are improved. In the invention described in claim 7, in the invention described in any one of claims 1 to 6, the reciprocating member is a piston.

The piston is used in various devices,
Since the processing accuracy is generally high, the processing accuracy can be relatively easily increased even when used for a viscous heater.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION

(First Embodiment) A first embodiment in which the present invention is embodied in a viscous heater incorporated in a vehicle heating apparatus will be described below with reference to FIGS.

As shown in FIG. 1, a front housing 11, a front side cylinder block 12, a rear side cylinder block 13 and a rear plate 14 constituting the housing extend through the cylinder blocks 12, 13 from the front housing 11. It is fastened by a plurality of bolts 15 screwed to the rear plate 14. The two cylinder blocks 12, 13 are provided with inner cylinders 12i, 1
3i and outer cylinders 12o and 13o, respectively. The inner cylinder 12i is in the front housing 11, and the inner cylinder 13i is in the rear plate 1.
4 are respectively positioned and fixed via positioning pins 15a. In this embodiment, each inner cylinder 1
2i and 13i are positioned and fixed via a plurality of (only one is shown) positioning pins 15a. A gasket 16 for sealing is interposed between the two cylinder blocks 12 and 13. Gaskets 17 are disposed between the front housing 11 and the cylinder block 12 and between the cylinder block 13 and the rear plate 14, respectively.

A chamber 18 is formed on the opposite surface of the inner cylinders 12i and 13i.
Shaft holes 12a and 13a are formed in the center of the shaft 13. The inner cylinders 12i, 13i have shaft holes 12a,
A plurality of cylinder bores 12b, 1
3b are formed to penetrate in parallel with each other, and a plurality of passages 19 communicating the chamber 18 with the outside are formed. A drive shaft 20 serving as a drive shaft constituting the drive means is rotatably supported via radial bearings 21 and 22 so as to penetrate the front housing 11 and cross the chamber 18. As the radial bearing 21 disposed on the front housing 11 side, a bearing having a shaft sealing function (for example, a bearing with a lip seal) is used.

A double-headed piston 23 as a reciprocating member is inserted into the cylinder bores 12b and 13b.
The peripheral surface of the cylindrical portion of the piston 23 and the cylinder bores 12b, 13
b Clearance to the inner surface (side clearance) is 1m
m or less, for example, a predetermined value of 0.2 to 0.5 mm. The length of the cylindrical portion forming each head of the piston 23 is formed to be substantially the same as the length of the cylinder bores 12b and 13b. A swash plate 24 as a cam plate constituting a driving means is supported at an intermediate portion of the driving shaft 20 so as to be integrally rotatable. Thrust bearings 25 are interposed between the boss 24a of the swash plate 24 and the cylinder blocks 12, 13, respectively. Each piston 23 is moored to the swash plate 24 via a pair of shoes 26, and the rotation of the swash plate 24 accompanying the rotation of the drive shaft 20 causes the piston 23 to reciprocate in the cylinder bores 12b and 13b. I have. The cylinder bores 12b, 13b and the chamber 18 constitute a heat generating chamber.

On the surfaces of the front housing 11 and the rear plate 14 facing the inner cylinders 12i, 13i, there are formed recesses 11a, 14a which allow the passage 19 to communicate with the cylinder bores 12b, 13b. Cylinder bores 12b, 13b, chamber 18, passage 19 and recess 11
The viscous fluid is accommodated in a and 14a. Silicone oil, mechanical oil, or the like is used as the viscous fluid.

The distance between the outer circumferences of the inner cylinders 12i and 13i and the inner circumferences of the outer cylinders 12o and 13o is shown in FIG.
As shown in FIG. 1, an annular water jacket 27 is formed so as to surround substantially half the circumference of each of the cylinder bores 12b and 13b. The water jacket 27 is formed as grooves 28 and 29 in which the chambers 18 of the cylinder blocks 12 and 13 are open. The water jacket 27 forms a heat radiating chamber adjacent to the heat generating chamber. A water inlet port 30 for taking in circulating water as a circulating fluid from the heating circuit (not shown) provided in the vehicle to the water jacket 27 is formed in the outer peripheral portion of the cylinder block 12 on the front side. A water outlet port 31 for sending circulating water from the water jacket 27 to the heating circuit is formed in the outer peripheral portion of the rear cylinder block 13.

The water jacket 27 is arranged so that the circulating water introduced from the water inlet port 30 flows evenly throughout the water jacket 27 and is discharged from the water outlet port 31.
Inside, spiral ridges 28a and 29a are formed.
The ridges 28a and 29a are provided on the inner wall surface of the water jacket 27, that is, on the side close to the cylinder bores 12b and 13b. The tips of the ridges 28a and 29a are formed in a state where there is a gap between the ridges 28a and 29a.

An electromagnetic clutch 32 is provided between an end of the drive shaft 20 protruding from the front housing 11 and a support cylinder 11b protruding from the front housing 11. The electromagnetic clutch 32 is slidably provided on a pulley 34 rotatably supported on the support cylinder 11 b via an angular bearing 33 and on a support ring 35 fixed to the outer end of the drive shaft 20. And a disk-shaped clutch plate 36. Clutch plate 36
A leaf spring 37 is provided on the back side of the. Leaf spring 3
7 is fixed to the support ring 35 at a substantially central portion thereof, and its outer end (upper and lower ends in FIG. 1) is connected to the outer peripheral portion of the clutch plate 36 by rivets or the like.
The front surface of the clutch plate 36 is opposed to the end surface 34a of the pulley 34, and the end surface 34a of the pulley 34 functions as another clutch plate.

The pulley 34 is operatively connected to an engine (not shown) of the vehicle as an external drive source via a belt. The front housing 11 supports an annular solenoid coil 38. The clutch plate 36 is pressed against the end face 34a of the pulley 34 by the excitation / demagnetization control of the solenoid coil 38, or the pressure is released, whereby the pulley 34 and the drive shaft 20 are connected or the connection is released. Is done. By connecting the pulley 34 and the drive shaft 20, the drive shaft 20 is rotated by the vehicle engine.

Next, the operation of the viscous heater configured as described above will be described. When the vehicle engine is driven, the electromagnetic clutch 32 is turned on and the drive shaft 2
0 is rotated, the swash plate 24 in the chamber 18 is rotated, and the plurality of pistons 23 are
It is reciprocated in 2b and 13b. Each piston 23 reciprocates in a state where a viscous fluid exists between the outer peripheral surface and the wall surfaces of the cylinder bores 12b and 13b. Since the gap between the piston 23 and the wall surfaces of the cylinder bores 12b and 13b is very narrow, when the piston 23 reciprocates, a frictional force (fluid frictional force) is generated by shearing the viscous fluid, and the viscous fluid generates heat. Then, the heat is transferred to the cylinder bore 12b,
Heat is exchanged with circulating water by a water jacket 27 provided outside 13b.

When each head end face of the piston 23 moves away from the opposing front housing 11 or rear plate 14, viscous fluid flows into the cylinder bore, and when it moves to the opposite side, the viscous fluid flows through the cylinder bore. Exhausted from inside. For example, FIG. 1 shows a state where the illustrated piston 23 has moved from the rear side to the front side,
At this time, the viscous fluid in the viscous heater generates a flow in the direction of the arrow shown in the figure. When the swash plate 24 further rotates from this state, the illustrated piston 23 starts moving toward the rear side, and the flow of the viscous fluid is reversed. The viscous fluid existing in the gap between the peripheral surface of the piston 23 and the wall surfaces of the cylinder bores 12b and 13b is replaced with the viscous fluid in the cylinder bore or the chamber 18 with the reciprocating motion of the piston 23, and only the specific viscous fluid is removed. It will not be subjected to shearing action.

As the piston 23 reciprocates, the viscous fluid is discharged from the cylinder bores 12b and 13b.
is discharged to a. Therefore, unlike the swash plate type compressor, a large thrust force is not applied to the thrust bearing 25.
Therefore, there is no adverse effect even if a silicone oil, which is not very suitable as a lubricating oil, is used as a viscous fluid.

The amount of heat generated by the viscous heater depends on the fluid frictional force. Piston 2 when piston 23 moves
The velocity distribution of the viscous fluid existing between the peripheral surface of the cylinder 3 and the cylinder bore wall surface is as shown in FIG. 3, and the fluid frictional force Ff per one side of the piston is expressed by the following equation.

Ff = −μA (dv / dy) = − μA (v ₀ / s) (1) where μ is the viscosity coefficient of the viscous fluid, and A is the surface area of the peripheral surface of the piston 23 in the cylinder bore. , v ₀ is the velocity of the viscous fluid adhering to the peripheral surface of the piston 23, s is the clearance between the peripheral surface of the cylinder bore wall and piston 23.

Assuming that the diameter of the piston 23 is D and the length of one side of the piston 23 in the cylinder bore is L,
A = πDL. The length L changes with the rotation of the swash plate 24. Assuming that the angular velocity of the drive shaft 20 is ω, L is ω
It is a function of t (t is time). The speed v ₀ is equal to the moving speed v of the piston 23, and is a bore pitch radius (the shortest distance between the axis of the drive shaft and the axis of the cylinder bore).
Is Bp and the angular velocity of the drive shaft 20 is ω, v ₀
= Bpωsin (ωt). As a result, equation (1) becomes the following equation.

Ff = −μπDL {Bpωsin (ωt)} / s (2) That is, the fluid frictional force Ff is proportional to the product of the bore pitch radius Bp, the piston diameter D, and the reciprocal of the gap s. Calorific value to Q ₁ viscous heater per one cylinder bore, corresponds to the work done against the fluid friction force Ff. (Q = nQ _{1 with} n cylinder bores) For this reason, the calorific value Q is proportional to the fluid frictional force Ff. Therefore, the calorific value Q is also proportional to the product of the bore pitch radius Bp, the piston diameter D, and the reciprocal of the gap s. When manufacturing a viscous heater, the probability that the processing accuracy or error varies from Bp, D and s to the side where the value of Q is increased or to the side where the value of Q is decreased is extremely small. The variation in the heating capacity is reduced as compared with the conventional viscous heater.

The viscous heater of this embodiment has the following effects. (A) In order to use the fluid friction heat generated by the reciprocating motion of the piston 23 (reciprocating member) in a state in which the viscous fluid is interposed between the cylinder bores (heating chambers) 12b and 13b, the conventional viscous heater is used. Even if the variation in processing accuracy is the same, the variation in heating capacity is reduced.

(B) Piston 23 as reciprocating member
Is used in various devices, and the processing accuracy thereof is generally high. Therefore, the piston 23 used for the viscous heater can be manufactured relatively easily with high processing accuracy. Since the cross section of the piston 23 is circular, it is easier to increase the processing accuracy.

(C) Since the driving means for reciprocating the piston 23 is constituted by the drive shaft 20 and the swash plate 24 supported so as to be integrally rotatable on the drive shaft 20, the plurality of pistons 23 are relatively small. Can be driven in space. As a result, the total surface area of the peripheral surface of the piston can be increased as compared with a configuration in which one piston is provided in a housing of the same size.

(D) The viscous fluid subjected to the shearing action, that is, the viscous fluid existing between the peripheral surface of the piston 23 and the wall surface of the cylinder bore, becomes viscous fluid in the cylinder bore or the chamber 18 as the piston 23 reciprocates. Is replaced by
Therefore, only the specific viscous fluid is not continuously subjected to the shearing action for a long time, so that it is possible to prevent the viscous fluid from being deteriorated due to excessive heat generation.

(E) Since the piston 23 is a double-headed type, the force acting on the swash plate 24 is balanced back and forth, and the durability is lower than that of a single-sided piston having the same surface area on the peripheral surface of the piston. improves.

(F) The water jacket 27 is annular and formed to be long in the axial direction of the drive shaft 20. The circulating water is guided inside the water jacket 27 by spiral ridges 28a and 29a. Since the water is circulated in the forward path, a short circuit or stagnation of the flow path of the circulating water in the water jacket 27 can be reduced. Therefore, heat exchange from the viscous fluid in the cylinder bores 12b, 13b and the chamber 18 to the circulating water in the water jacket 27 can be efficiently performed.

(G) Since the ridges 28a and 29a are formed so as to protrude into the water jacket 27 from the heat generating chamber side, the contact area between the circulating water in the water jacket 27 and the wall surface around the heat generating chamber is reduced. And heat exchange efficiency is improved. Further, since the tips of the ridges 28a and 29a do not contact the opposing surface, heat is not directly transmitted to the outside of the water jacket 27 via the ridges 28a and 29a, and the heat exchange efficiency with the circulating water is reduced. Is improved.

(H) Since the water jacket 27 is formed not to have a simple cylindrical shape but to extend along the peripheral surfaces of the cylinder bores 12b and 13b, the heat exchange efficiency is improved.

(Second Embodiment) Next, a second embodiment will be described with reference to FIG. This embodiment differs greatly from the previous embodiment in that a crank mechanism is used instead of the swash plate 24 as driving means for the reciprocating member and one piston is used.

The housing comprises a cylinder block 39,
The bottom plate 40 arranged on the lower side and the top housing 41 arranged on the upper side are fastened by bolts 42. The cylinder block 39 includes an inner cylinder 39i and an outer cylinder 39o. An O-ring 43a is interposed between the bottom plate 40 and the cylinder block 39, and a gasket 43b is interposed between the top housing 41 and the cylinder block 39. Further, an O-ring 39a is interposed between the inner peripheral surface of the end of the outer cylinder 39o on the bottom plate 40 side and the outer peripheral surface of the inner cylinder 39i. A piston 45 is accommodated in the cylindrical cylinder bore 44 of the inner cylinder 39i so as to be able to reciprocate with a predetermined gap from the inner peripheral surface of the inner cylinder 39i. The cylinder bore 44 constitutes a heat generating chamber.

The top housing 41 has a support cylinder portion 41a through which a crankshaft 46 as a drive shaft can be inserted and a hole 41.
The crankshaft 46 is rotatably supported by the top housing 41 via radial bearings 47 and 48 fitted in the support cylinder 41a and the hole 41b. One end of the crankshaft 46 protrudes from the support cylinder 41a, and is operatively connected to the engine of the vehicle via a clutch (not shown) similar to the electromagnetic clutch of the embodiment. Bearings with lip seals are used for the radial bearings 47 and 48. The support cylinder portion 41a is formed to have an inner diameter that allows the crank portion of the crankshaft 46 to be inserted.

The piston 45 is formed in a cylindrical shape, is connected to the crankshaft 46 via a piston pin 49 and a connecting rod 50, and reciprocates in the vertical direction as the crankshaft 46 rotates. Viscous fluid is cylinder block 3
Approximately half the volume of 9 is accommodated. Driving means is constituted by the crankshaft 46, the piston pin 49 and the connecting rod 50.

A water jacket 51 is formed between the inner cylinder 39i and the outer cylinder 39o. A water inlet port 52 and a water outlet port 53 are formed in the outer cylinder 39o. The water jacket 51 is formed as a cylindrical groove with the top housing 41 side open, and a spiral guide ridge 54 projecting from the outer peripheral surface of the inner cylinder 39i is provided in the water jacket 51.

In this embodiment, when the engine is driven, the electromagnetic clutch is turned on and the crankshaft 46 is turned on.
Is rotated, the piston 45 is reciprocated via the connecting rod 50 and the piston pin 49 in a state where a viscous fluid exists between the piston 45 and the peripheral surface of the cylinder bore 44. Then, similarly to the above embodiment, a frictional force (fluid frictional force) by shearing the viscous fluid acts, and the viscous fluid generates heat. Then, the heat is exchanged with the circulating water in the water jacket 51.

This embodiment has the following effects in addition to the effects of (A), (B), (D), (F) and (G) among the effects of the above embodiment. (I) A relatively large surface area that contributes to fluid friction of a viscous fluid can be obtained with one piston 45, and the structure is simplified.

(G) Since the piston 45 is formed in a cylindrical shape, that is, in such a shape that viscous fluid existing before and after in the moving direction of the piston can pass through the inside of the piston, a member for closing the end of the cylinder block 39 There is no need to provide a viscous fluid storage section in the bottom plate 40 in this embodiment, which contributes to downsizing the viscous heater.

(G) Since the driving means for the piston 45 is disposed above the cylinder block 39 and the viscous fluid is contained in a portion of the cylinder block 39 corresponding to the movement range of the piston 45, the amount of the viscous fluid is reduced. It does not need to increase unnecessarily.

(Third Embodiment) Next, a third embodiment will be described with reference to FIGS. In this embodiment, the reciprocating movement of the piston using the swash plate is the same as in the first embodiment, but the point that the stroke of the piston can be changed and the point that the piston is a single-headed piston are large. Is different.

As shown in FIG.
5 is a cylinder block 56 and an external rear housing 57
Is joined and fixed to the front end via a gasket 58.
At the rear end of the cylinder block 56, an inner rear housing 5 is provided.
9 is joined and fixed via a gasket 60 and a valve plate 61. The front housing 55, the cylinder block 56, the valve plate 61, and the inner rear housing 59 are fastened and fixed by bolts 15. Also, the front housing 55 and the external rear housing 57
Are fixed by bolts (not shown).

Crank chamber 62 as a chamber for accommodating swash plate
Is surrounded by a front housing 55 and a cylinder block 56. The drive shaft 20 is rotatably supported via the radial bearing 22 between the front housing 55 and the cylinder block 56 so as to cross the crank chamber 62. A shaft sealing device (oil seal) 63 is interposed between the front end side of the drive shaft 20 and the front housing 55. Drive shaft 20
Are connected to an external drive source (engine) (not shown) via an electromagnetic clutch.

A substantially disk-shaped rotating support (lug plate) 64 is provided within the crank chamber 62 for the drive shaft 2.
0 so as to be integrally rotatable. The swash plate 65 is supported on the drive shaft 20 so as to be slidable and tiltable in the axial direction. A pair of support arms 66 (only one side is shown) constituting a hinge mechanism are provided on the rotary support 64.
Is protruding. A pair of guide pins 67 also constituting a hinge mechanism protrude from the front side of the swash plate 65, and a spherical portion 67 a provided at the tip of each guide pin 67 is provided with a guide hole provided in each support arm 66. 66a is slidably fitted in 66a. That is, the swash plate 65 is connected to the rotary support 64 via the hinge mechanism so as not to rotate relatively.

The swash plate 65 can be tilted in the axial direction of the drive shaft 20 and can rotate integrally with the drive shaft 20 by the cooperation of the support arm 66 and the guide pin 67. The swash plate 65 has a slide guide relationship between the guide hole 66a and the spherical portion 67a and the drive shaft 2.
It is tilted by the zero slide support action. When the rotation center of the swash plate 65 is moved to the cylinder block 56 side,
The inclination angle (inclination angle) θ of the swash plate 65 is reduced.

Coil spring 6 as inclination decreasing spring
The coil spring 68 is wound around the drive shaft 20 between the rotary support 64 and the swash plate 65.
Urges the swash plate 65 in the direction of decreasing the inclination angle. The ring-shaped stopper 69 is fixed to the drive shaft 20 between the swash plate 65 and the cylinder block 56, and the swash plate 65 abuts on the stopper 69, thereby defining the minimum inclination angle of the swash plate 65. An inclination restricting projection 70 is integrally formed on the front side of the swash plate 65, and the maximum inclination angle of the swash plate 65 is
Is in contact with the rotating support 64.

A plurality of cylinder bores 56a (only two are shown in FIG. 5) are formed in the cylinder block 56, and the same number of single-headed pistons (hereinafter simply referred to as pistons) 71 are accommodated in the cylinder bore 56a. The swash plate 65 is engaged with the piston 71 via the shoe 26,
5 is converted into a reciprocating motion of the piston 71 back and forth.

A chamber 72 is formed between the valve plate 61 and the inner rear housing 59. A suction hole 61a and a discharge hole 61b are formed in the valve plate 61 at positions corresponding to the respective cylinder bores 56a. A suction hole 6 is provided in the cylinder bore 56a side of the valve plate 61.
A suction valve 73 for opening and closing 1a is fixed to the chamber 72 side, and a discharge valve 74 and a retainer 75 for opening and closing the discharge hole 61b are fixed by bolts 76 and nuts 77. The viscous fluid in the chamber 72 is sucked into the cylinder bore 56a via the suction hole 61a and the suction valve 73 by the reciprocating operation of the piston 71. The viscous fluid that has flowed into the cylinder bore 56a is discharged to the chamber 72 via the discharge hole 61b and the discharge valve 74 by the forward movement of the piston 71. The opening of the discharge valve 74 is defined by a retainer 75.

A thrust bearing 78a, which bears a thrust load acting on the drive shaft 20 with the reciprocating movement of the piston 71, comprises a rotary support 64 and the front housing 5
5 and the inner wall surface. A thrust bearing 78b is also provided in a housing formed at the center of the cylinder block 56.

A water jacket 79 as a heat radiating chamber is provided between the outer peripheral surface of the cylinder block 56, the outer surface of the inner rear housing 59, and the inner surface of the outer rear housing 57.
Are formed. On the outer surface of the inner rear housing 59, a plurality of annular ridges 59a are formed concentrically. A water inlet port 30 and a water outlet port 31 are formed on the outer peripheral portion of the outer rear housing 57.

The crank chamber 62 is connected to a pressure adjusting means 80 as a swash plate angle changing means via a pipe (pipe) 81. The end of the pipe 81 is connected to the front housing 55.
Are connected in an oil-tight manner via a seal member (for example, an O-ring) 82, and the pressure adjusting means 80 and the crank chamber 62 are communicated with each other. The pressure adjusting means 80 includes a cylinder 83, a piston 84 slidably accommodated in the cylinder 83, an electric cylinder 85 for reciprocatingly driving the piston 84, and a control device 86 for controlling the electric cylinder 85. . An O-ring 84a for sealing is accommodated in a groove formed on the outer periphery of the piston 84. The electric cylinder 85 combines a motor and a screw, and takes out the rotational force of the motor as a linear thrust. For example, the rotor of the motor is hollow,
A male screw as an output shaft 85a penetrates therein and is arranged so as to be non-rotatable and movable in the axial direction. A female screw that is screwed with the male screw is attached to the rotor. The control device 86 stores the relationship between the rotational speed of the drive shaft 20, the room temperature, and the like, and the appropriate pressure in the crank chamber 62. Then, the controller 86 controls the drive shaft 20
The amount of heat generated is controlled by adjusting the pressure in the crank chamber 62 according to the operating state, such as the rotation speed and room temperature.

The controller 86 adjusts the pressure so that the angle formed between the swash plate 65 and the drive shaft 20 at the time of activation of the viscous heater increases, that is, the inclination angle θ decreases.

In this embodiment, machine oil is used as the viscous fluid, and the viscous fluid is supplied to the crank chamber 62 and the chamber 7.
2. The cylinder bore 56a, the pipe 81 and the cylinder 83 are filled.

The viscous heater of this embodiment also generates heat by the reciprocating movement of the piston 71 through the swash plate 65 by the rotation of the drive shaft 20, as in the first embodiment. The reciprocating motion of the piston 71 compresses the viscous fluid, and the piston 71 and the cylinder bore 56a
Generates heat due to the viscous fluid friction in the side clearance. When the piston 71 moves toward the chamber 72, the viscous fluid receives a compressing action, and the compressed viscous fluid presses and moves the discharge valve 74 to be discharged from the discharge hole 61b to the chamber 72. When the piston 71 moves backward, the viscous fluid in the chamber 72 presses and moves the suction valve 73 to flow into the cylinder bore 56a. The theoretical heating value Q of the viscous heater of this embodiment is expressed by the following equation.

Q = VΔp (heat generated by pressurization) + heat generated by viscous fluid friction in side clearance where Δp is the differential pressure between the pressure of chamber 72 and the discharge pressure
V is the discharge amount.

The stroke of the piston 71 changes depending on the inclination angle θ of the swash plate 65. As the inclination angle θ increases, the stroke increases and the amount of heat generated per rotation of the drive shaft 20 increases. The inclination angle θ of the swash plate 65 changes depending on the pressure in the crank chamber 62. The inclination angle θ decreases as the pressure in the crank chamber 62 increases, and the inclination angle θ decreases as the pressure decreases.
Becomes larger.

The controller 86 activates the viscous heater with the output shaft 85a of the electric cylinder 85 moved to the maximum projecting position. In this case, the pressure in the crank chamber 62 is increased to the maximum pressure, and as shown in FIG.
Is minimized, the drive shaft 20 is rotated. As a result, the stroke of the piston 71 is minimized, and the starting torque is reduced. Thereafter, in order to increase the amount of heat generated when the drive shaft 20 rotates at a low speed, the control device 86 drives the electric cylinder 85 in a direction in which the output shaft 85a is immersed, and lowers the pressure in the crank chamber 62. As a result, the swash plate 65
Changes through the intermediate state shown in FIG. 6 to the maximum position shown in FIG. In the state shown in FIG.
5 becomes the maximum, the stroke of the piston 71 becomes the maximum, and the necessary heat generation can be secured even at low speed rotation.

Further, the control device 86 controls the electric cylinder 85 to rotate the output shaft 85a in order to suppress excessive heat generation during high-speed rotation.
Are driven in the direction in which the protrusions protrude to increase the pressure in the crank chamber 62. As a result, the inclination angle θ of the swash plate 65 becomes small, and FIG.
In this case, the stroke of the piston 71 is reduced and the amount of heat generation is reduced.

This embodiment has the following effects in addition to the effects (a) to (d) among the effects of the first embodiment. (ヲ) Since the swash plate 65 is provided with a swash plate angle changing means for changing the inclination angle θ of the swash plate 65, by adjusting the inclination angle θ, it is possible to prevent an excessive amount of heat generation at a high speed, and a shaft sealing device. 63 and the like, and the durability and reliability are improved. In addition, a necessary heat generation amount can be ensured even at low speed rotation.

(C) The swash plate angle changing means is configured to change the inclination angle θ of the swash plate 65 by changing the pressure of the viscous fluid in the crank chamber 62 in which the swash plate 65 is accommodated, so that the structure is simple. Become.

(F) Since the engine is started when the inclination angle θ is small, the torque required to drive the drive shaft 20 at the time of startup is reduced, the shock when the electromagnetic clutch is connected is reduced, and the startup is smooth. Done.

(4) Since machine oil is used as the viscous fluid, the radial bearing 22, the shoe 26, the spherical portion 67a, the thrust bearings 78a, 78b, etc. are well lubricated, and the sliding portions and bearings The durability is improved.

(G) The control device 86 controls the drive shaft 20
The amount of heat generated is controlled by adjusting the pressure in the crank chamber 62 according to the operating state, such as the rotation speed and room temperature of the motor, so that an extra load is prevented from being applied to the drive source, and unnecessary power consumption is reduced. .

The embodiments are not limited to the above embodiments, but can be embodied as follows, for example. (1) In a configuration in which a swash plate similar to that of the first embodiment is used as the piston driving means, a configuration in which a single-headed piston 71 is used as shown in FIG. . In this case, the cylinder block 12 on the front side of the viscous heater according to the first embodiment is shortened, and the concave portion 11a of the front housing 11 and the passage 19 of the cylinder block 12 become unnecessary. A groove 71a is formed on the base end side peripheral surface of the piston 71, so that a load is hardly applied to the base end side surface of the piston 71 when the piston 71 moves. In this configuration, the viscous heater is smaller in size than the one using a double-headed piston.

(2) In the configuration of the first embodiment and (1), the pistons 23 and 71 are provided with
As shown in (1), passages 23a and 71b are formed to communicate the distal end surfaces of the pistons 23 and 71 and the chamber 18. In this configuration, when the pistons 23 and 71 move, the viscous fluid
a, 71b and the inside of the cylinder bores 12b, 13b and the chamber 1
8 and move smoothly. Therefore, when this configuration is adopted, it is not necessary to form the passage 19 in the cylinder blocks 12, 13, and the concave portions 11a, 14a of the front housing 11 and the rear plate 14 are also unnecessary.
The structure is simplified, and the manufacturing cost can be reduced.

(3) As shown in FIGS. 10A and 10B, the distal ends of the pistons 23 and 71 are formed in a cylindrical shape, and the passages 23a and 71b are formed. Convex part 8 that can be inserted into cylindrical part
7, 88 are formed such that there is a gap between the inner peripheral surface of the cylindrical portion and the gap between the outer peripheral surface of the piston and the peripheral surface of the cylinder bore. In this case, the amount of heat generated by one reciprocation of the pistons 23 and 71 increases.

(4) In the configuration in which the piston 45 is reciprocated by the crank mechanism as in the second embodiment,
As shown in FIG. 11, the piston 45 is formed in a completely cylindrical shape, and the piston pin 49 is provided at a position away from the tip of the piston 45. And the bottom plate 40
An intermediate block 89 having a projection 89a inserted into the piston 45 is provided between the cylinder block 39 and the cylinder block 39.
A gap is formed between the peripheral surface of the convex portion 89a and the inner peripheral surface of the piston 45, the size of which effectively generates shear heat.
Further, a cylindrical water jacket 90 independent of the water jacket 51 is formed in the intermediate block 89.
The circulating water of the heating circuit flows through the water jacket 90 via an inlet port and an outlet port (not shown). In this case, the amount of heat generated by one reciprocation of the piston 45 increases, and the generated heat is efficiently exchanged with the circulating water. (5) In (4), the water jacket 90 may be omitted. In this case, the bottom plate 40 becomes unnecessary, and the structure is simplified as compared with (4).

(6) Instead of a swash plate as a cam plate, for example, JP-A-7-97978 and JP-A-7-17-1
A cam plate as used in a wave cam type compressor disclosed in, for example, Japanese Patent No. 89901 may be used.

(7) As in the case of the swash plate type (wobble type) compressor, the piston may be reciprocated by using a swash plate that only swings in a state where rotation is restricted. (8) In the case of a configuration in which the piston reciprocates via the swash plate, unlike the compressor, the thrust force applied to the swash plate and the drive shaft is small, so the thrust bearing 25 may be omitted. In this case, the radial bearings 21 and 22
Preferably, an angular bearing is used.

(9) In the second embodiment, the crankshaft 46 may be arranged below the piston 45. That is, it is used by being arranged upside down in the same configuration as in FIG. However, the viscous fluid is the crankshaft 46
Needs to be filled in the chamber in which is stored and in the cylinder bore 44 of the cylinder block 39. Moreover, you may arrange | position horizontally and use it.

(10) The cylinder bores 12b, 13b,
The cross-sectional shape of the piston 44, 45, 7 may be, for example, a triangle, a quadrangle, a hexagon, an ellipse, or the like other than a circle.
The outer shape of 1 may be a shape corresponding thereto.

(11) Water jackets 27 and 51
In place of the spiral ridges 28a, 29a, 54, ridges extending in parallel with the movement direction of the piston are provided in a staggered manner.
In this case, the production of the ridge becomes easy.

(12) Also, the ridges 28a, 29a, 5
4 may be formed such that its tip abuts on the opposing surface, or the ridges 28a, 29a, 54 may be omitted. (13) The water jacket 27 may be formed in a simple cylindrical shape, or may be formed in a square cylindrical shape or a polygonal cylindrical shape corresponding to the shape or arrangement of the cylinder bore.

(14) By omitting the electromagnetic clutch 32,
Pulley 34 is attached to drive shaft 20 or crankshaft 46.
And the pulley 3
Alternatively, the drive shaft may be directly transmitted to the drive shaft via the drive shaft 4.

(15) As the radial bearing 21, a normal bearing may be used instead of the bearing having the shaft sealing function, and an oil seal may be used together. (16) In the third embodiment, valve mechanisms such as the suction valve 73 and the discharge valve 74 may be omitted. In the first embodiment and (1), a valve mechanism such as a suction valve and a discharge valve may be provided.

(17) As the reciprocating member, a belt wound around a pair of pulleys (rollers) accommodated in the housing and reciprocated with the reciprocating rotation of the pulley may be used.

Incidentally, the “viscous fluid” referred to in this specification is
It means any medium that generates heat based on fluid friction under the shearing action of the "reciprocating member", and is not limited to high-viscosity liquids or semi-fluids, and is not limited to silicone oil. Absent. Also, "piston"
Is a member that reciprocates along the wall surface of a chamber (cylinder bore) that contains a viscous fluid, and is not limited to a so-called piston that moves in the same direction as the fluid in the room in a state where the chamber is partitioned.
It includes a member through which the fluid in the chamber can pass through the inside of the reciprocating member, such as a cylindrical member (piston) or a member in which a hole is formed in the piston in the axial direction.

The technical ideas (inventions) other than those described in the claims which can be understood from the above embodiments are described below together with their effects. (1) In the invention described in claim 1, the driving means transmits the rotational force of the external driving source to the reciprocating member by a crank mechanism. In this case, a relatively large surface area that contributes to the fluid friction of the viscous fluid can be obtained with one reciprocating member, and the structure is simplified.

(2) In the invention described in (1), the reciprocating member is a piston. In this case, a piston with high processing accuracy can be easily manufactured. (3) In the invention described in (2), the piston is configured to reciprocate below the crank mechanism, and the viscous fluid fills the movement range of the piston. In this case, the filling amount of the viscous fluid may be small.

(4) In the invention according to any one of claims 7, (2) and (3), a passage through which a viscous fluid can move inside the piston when the piston moves is formed. In this case, the viscous fluid is not compressed when the piston moves, and the piston can be easily reciprocated with a small driving force.

[0093]

As described in detail above, according to the first to seventh aspects of the present invention, it is possible to reduce the variation in the heating capacity due to the variation in the processing accuracy.

According to the second aspect of the present invention, a plurality of reciprocating members (pistons) can be driven in a relatively small space, and the pistons can be moved as compared with a configuration in which one piston is provided in a housing of the same size. The total surface area of the peripheral surface can be increased, and the amount of heat generated per rotation of the drive shaft can be increased.

According to the third aspect of the invention, the swash plate angle is changed by the swash plate angle changing means, so that the amount of heat generated during high-speed rotation is prevented from being excessive, and the durability of the oil seal and the like is improved. . Further, it is possible to secure a necessary heat generation amount even at low speed rotation.

According to the fourth aspect of the present invention, the swash plate angle changing means changes the swash plate angle by changing the pressure in the room in which the swash plate is housed, so that the structure is simplified. According to the fifth aspect of the present invention, since the startup is performed with the swash plate angle being small, the torque required to drive the drive shaft at startup is reduced, and the shock when the electromagnetic clutch is connected is reduced. , Startup is performed smoothly.

According to the sixth aspect of the invention, the mechanical oil is used as the viscous fluid, so that the durability of each sliding portion and bearing is improved. According to the seventh aspect of the invention, the reciprocating member can be manufactured relatively easily with high processing accuracy.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a viscous heater according to a first embodiment.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a schematic diagram showing a velocity distribution of a viscous fluid.

FIG. 4 is a sectional view showing a viscous heater according to a second embodiment.

FIG. 5 is a sectional view showing a viscous heater according to a third embodiment.

FIG. 6 is a partial cross-sectional view of the same inclination angle.

FIG. 7 is a partial cross-sectional view showing a state where the inclination angle is the same.

FIG. 8 is a partial cross-sectional view showing a modified viscous heater.

FIG. 9 is a partial cross-sectional view showing a piston of a modified example.

FIG. 10 is a partial sectional view showing a piston according to another modification.

FIG. 11 is a sectional view showing a piston according to another modification.

[Explanation of symbols]

11, 55: Front housing constituting the housing, 12, 13, 56: Similarly, cylinder block, 12
i, 13i: an inner cylinder constituting a cylinder block; 12o, 13o: an outer cylinder, 12
b, 13b, 44, 56a: cylinder bores forming a heat generating chamber; 14: rear plates forming a housing;
... a drive shaft as a drive shaft constituting drive means, 2
3, 45, 71 ... piston as a reciprocating member, 2
4, 65: a swash plate as a cam plate constituting a driving means; 26, a shoe; 27, 51, 59, 79: a water jacket as a radiating chamber; 50: connecting rod constituting the driving means. 62: a crank chamber as a chamber; 64: a rotary support; 66: a support arm constituting a hinge mechanism;
7 ... Guide pins as well.

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

Claims (7)

[Claims] A reciprocating member disposed reciprocally in a state in which a viscous fluid is interposed between a heat generating chamber provided in a housing, a wall surface of the heat generating chamber, and driving the reciprocating member. A reciprocating viscous heater comprising: a driving unit; and a heat radiating chamber provided adjacent to the heat generating chamber and exchanging heat generated by the reciprocating motion of the reciprocating member with a circulating fluid. 2. The drive means includes a drive shaft for transmitting a rotational force of an external drive source, and a cam plate for transmitting reciprocating motion to the reciprocating member via a shoe with rotation of the drive shaft. The reciprocating viscous heater according to claim 1. 3. The swash plate according to claim 2, wherein the cam plate is a swash plate supported so as to be tiltable on the drive shaft, and swash plate angle changing means for changing an inclination angle of the swash plate. Reciprocating viscous heater. 4. The swash plate is rotatably connected to a rotation supporter rotatably supported by the drive shaft via a hinge mechanism, and the swash plate angle changing means accommodates the swash plate. 4. The reciprocating viscous heater according to claim 3, wherein said viscous heater is a pressure adjusting means which is communicated with said chamber and adjusts the pressure inside said chamber. 5. The reciprocating viscous heater according to claim 3, wherein the swash plate angle changing means adjusts the swash plate angle so that the angle between the swash plate and the drive shaft increases at the time of startup. 6. The reciprocating viscous heater according to claim 2, wherein a mechanical oil is used as the viscous fluid. 7. The reciprocating viscous heater according to claim 1, wherein the reciprocating member is a piston.