WO1998033671A1

WO1998033671A1 - Reciprocating type viscous heater

Info

Publication number: WO1998033671A1
Application number: PCT/JP1998/000396
Authority: WO
Inventors: Takahiro Moroi; Takashi Ban; Tatsuyuki Hoshino; Tatsuya Hirose
Original assignee: Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Priority date: 1997-01-31
Filing date: 1998-01-30
Publication date: 1998-08-06
Also published as: JPH10272917A; DE19880297T1

Abstract

A double-end piston is contained in a cylinder bore formed so as to communicate with a chamber in which a swash plate (24) is contained, in an inner cylinder forming a cylinder block. The swash plate is integratedly rotatably supported in the middle of a driving shaft, and each piston is anchored to the swash plate through a shoe. A water jacket is formed between the inner cylinder and an outer cylinder. The piston is reciprocated inside the cylinder bore by the rotation of the swash plate following the rotation of the drive shaft, and heat generated by the fluid friction of a viscous fluid interposed between the circumferential surface of the piston and the wall surface of the cylinder bore is transferred to circulating water inside the water jacket by heat exchange.

Description

eft H letter

Reciprocating viscous heater

Technical field

The present invention relates to a viscous heater. More specifically, a viscous heater that generates heat due to fluid friction in a viscous fluid contained in the heat generating chamber by the action of a member that moves in the heat generating chamber in the housing, and exchanges this heat with a circulating fluid flowing through the heat radiating chamber. Concerns. Background art

A viscous heat source that uses the driving force of the engine has attracted attention as a heat source for in-vehicle supplementary ribs. For example, Japanese Patent Laying-Open No. 2-264832 discloses a viscous heater incorporated in a vehicle heating device. In this viscous light, the front and rear housings are connected to each other in a state of being opposed to each other, and a heat generating chamber is formed inside the heat generating chamber, and a warm and cold jacket (heat discharging 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 the 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 between a wall surface of the heat generating chamber and a wall surface of the rotor. ing. 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 the viscous fluid interposed between the inner wall of the heating chamber and the outer wall of the rotor is sheared by the rotor to generate a fluid. Generates heat based on friction. The heat generated in the heat generating chamber is exchanged with the circulating water flowing in the jacket, and the heated circulating water is supplied to an external heating circuit to be used for heating the vehicle. In the above-mentioned conventional viscous heater, since it is necessary to form irregularities for labyrinth construction on the front and rear outer wall portions of the rotor, the rotor body is similar to a disk having a shaft length shorter than half a g from its axis. Shape. In such a rotor, the main shearing action surface is the uneven surface of the front and rear outer walls of the mouth, and the rotational speed (ie, the shearing speed) of the uneven surface located farther away from the axis of the main body. ) Increases. For this reason, in order to increase the calorific value of the heat source, it is necessary to increase the diameter of the low profile, that is, to increase the outer diameter of the main body. In addition, in a disk-type viscous heater, the calorific value is theoretically proportional to the fourth power of the radius, and the variation in the performance due to the variation of the radius, the degree of filling of the oil, the difference in the location of the oil, etc. increases. . In other words, variations in processing accuracy greatly affect the heating capacity of viscous heaters. As a result, if the heating capacity is increased in anticipation of the variation, that is, if the radius is set to a relatively large value, a problem occurs that the viscous fluid is easily overheated due to heat generation and deteriorates easily. Disclosure of the invention

The present invention has been made to solve the above-described problem, and an object of the present invention is to provide a viscous heater having uniform heating accuracy. In order to achieve the above object, the present invention provides a heat generating chamber provided in a housing, and a reciprocating member disposed so as to be able to reciprocate with a viscous fluid interposed between a wall surface of the ripening chamber. A driving means for driving the reciprocating member, and a 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. I do. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a sectional view showing a first embodiment of a viscous heater according to the present invention. FIG. 2 is a sectional view taken along line 2-2 in FIG. FIG. 3 is a schematic diagram showing a velocity distribution of a viscous fluid.

FIG. 4 is a sectional view showing a second embodiment of the viscous heater according to the present invention. FIG. 5 is a sectional view showing a third embodiment of the viscous heater according to the present invention. FIG. 6 is a partial cross-sectional view showing the swash plate in the embodiment shown in FIG.

FIG. 7 is a partial cross-sectional view showing the swash plate in a state where the inclination angle is the minimum.

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

FIG. 9 is a partial cross-sectional view showing a modified biston.

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

FIG. 11 is a sectional view showing a piston according to another modification. BEST MODE FOR CARRYING OUT THE INVENTION

(First Embodiment)

Hereinafter, a first embodiment in which the present invention is embodied in a viscous heater incorporated in a heating device of a vehicle will be described with reference to FIGS. As shown in FIG. 1, the front housing 11, the front cylinder block 12, the rear cylinder block 13, and the rear plate 14 pass through the cylinder block 12, 13 from the front housing 11 to the rear plate. It is fastened with a plurality of ports 15 screwed to 14. Both cylinder blocks 12 and 13 are composed of inner cylinders 12 i and 13 i and outer cylinders 12 ο and 13 ο, respectively. The inner cylinder 12 i is connected to the front housing 11 and the inner cylinder The cylinders 13i are fixed to the rear plate 14 via positioning pins 15a, respectively. Each of the inner cylinders 12i and 13i is positioned and fixed via a plurality of (only one is shown) positioning pins 15a. A gasket 16 for sealing is interposed between both cylinder ports 12 and 13. Also, Freon Gaskets 17 are disposed between the housing 11 and the cylinder block 12 and between the cylinder block 13 and the IL block 4, respectively. A chamber 18 is formed on the opposite surface of both inner cylinders 12 i, 13 i, and shaft holes 12 a, 13 a are formed in the center of the cylinder works 12, 13. In the inner cylinders 12i, 13i, a plurality of cylinder bores 12b, 13b are formed at equal intervals around the shaft holes 12a, 13a, and penetrate in parallel with each other. A passage 19 is formed. A drive shaft 20 as a drive shaft constituting the drive means is rotatably supported via radial bearings 21 and 22 so as to pass through the front housing 11 and cross the chamber 18. For the radial bearing 21 disposed on the front housing 11 side, a bearing having a shaft sealing function (for example, a bearing with a rib seal) is used. A double-headed piston 23 as a reciprocating member is inserted into the cylinder bores 12b and 13b. The clearance (side clearance) between the peripheral surface of the cylindrical portion of the piston 23 and the inner surfaces of the cylinder pores 12b and 13b is set to a predetermined value of lmm or less, for example, 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 pores 12b and 13b. A swash plate 24 as a cam plate is rotatably supported at an intermediate portion of the drive shaft 20. Thrust bearings 25 are interposed between the boss portion 24a of the swash plate 24 and the cylinder ports 12 and 13, respectively. Each piston 23 is moored to the swash plate 24 via a pair of shoes 26. 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. It has become. The cylinder pores 12b, 13b and the chamber 18 constitute a heat generating chamber. Inner cylinder 12 i, 1 of front housing 1 1 and rear plate 14 Concave portions lla and 14a are formed on the surface facing 3i so that the passage 19 can communicate with the cylinder pores 12b and 13b. A viscous fluid is contained in the cylinder bores 12b, 13b, the chamber 18, the passage 19, and the recesses 11a, 14a. Silicone oil ゃ mechanical oil is used as the viscous fluid. As shown in FIG. 2, between the outer circumference of the inner cylinder 1 2 i, 13 i and the inner circumference of the outer cylinder 12 o, 13 o, approximately half the circumference of each cylinder bore 12 b, 13 b An annular water jacket 27 is formed so as to surround the water jacket. The air jacket 27 is formed as grooves 28, 29 with the chamber 18 side of each cylinder block 12, 13 open. The water jacket 27 constitutes 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 a heating circuit (not shown) provided in the vehicle to the water jacket 27 is formed on the outer peripheral portion of the cylinder block 12 on the front side. A water outlet port 31 for sending out circulating water from the heater jacket 27 to the heating circuit is formed on the outer peripheral portion of the cylinder block 13 on the rear side. A spiral ridge 2 is provided in the water jacket 27 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. 8 a and 29 a are formed. The ridges 28a and 29a project from the inner wall surface of the water jacket 27, that is, the outer peripheral surfaces of the inner cylinders 12i and 13i. The tips of the ridges 28a and 29a are formed so that 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 11 b protruding from the front housing 11. The electromagnetic clutch 32 is engaged with a pulley 34 rotatably supported on the support cylinder 11b via an angular bearing 33 and an outer end of the drive shaft 20. And a disk-shaped clutch plate 36 provided so as to be slidable on the support ring 35. On the back side of the clutch plate 36, a plate panel 37 is provided. The plate panel 37 is fixed to the support ring 35 at a substantially central portion thereof, and its outer ends (upper and lower ends in FIG. 1) are 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 a vehicle engine (neither is shown) via a belt. An annular solenoid coil 38 is supported by the front housing 11. The clutch plate 36 is pressed against the end surface 34 a of the pulley 34 by the excitation and demagnetization of the solenoid coil 38, and the press contact is released, so that the pulley 34 and the drive shaft 20 are separated from each other. Connected or disconnected. 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. First, when the electromagnetic clutch 32 is turned on while the vehicle engine is driven, and the drive shaft 20 is rotated, the swash plate 24 in the chamber 18 is rotated, and A plurality of pistons 23 are reciprocated in the cylinder pores 12b and 13b. Each piston 23 reciprocates in a state where a viscous fluid exists between its outer peripheral surface and the wall surfaces of the cylinder pores 12b and 13b. Since the gap between the piston 23 and the wall of the cylinder pores 1 2b, 13 b is very small, when the piston 23 reciprocates, a frictional force (fluid frictional force) is generated by shearing the viscous fluid. The fluid generates heat. Then, the heat is exchanged with the circulating water by the water jacket 27 provided outside the sealing pores 12b and 13b. The viscous fluid flows into the cylinder bore when moving in the direction away from the front housing 11 or rear plate 14 where the head end faces of the pistons 23 face each other, and viscous fluid when moving to the opposite side. Is discharged from the cylinder pores. For example, FIG. 1 shows a state in which the biston 23 shown in the drawing 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 to move toward the lya 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 surface of the cylinder bores 1 2 b and 13 b is replaced with the viscous fluid in the cylinder bore or the chamber 18 as the piston 23 reciprocates. However, only certain viscous fluids are not brought into a shearing state. As the piston 23 reciprocates, the viscous fluid is discharged from the cylinder pores 12b and 13b, but the viscous fluid is discharged to the concave portions 1la and 14a without receiving a large resistance. 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 suitable as a lubricating oil, is used as a viscous fluid. The calorific value of this viscous light depends on the fluid frictional force. The velocity distribution of the viscous fluid existing between the peripheral surface of the piston 23 and the cylinder pore wall when the piston 23 moves is shown in Fig. 3, and the fluid friction force F f per one piston Is expressed by the following equation.

F f =-A (d v / d) =-j A (vO / s)-(1)

Where is the viscosity coefficient of the viscous fluid and A is the piston in the cylinder bore.

3 is the surface area of the peripheral surface, νθ is the velocity of the viscous fluid attached to the peripheral surface of the piston 23, and s is the gap between the wall surface of the cylinder pore and the peripheral surface of the piston 23. If the diameter of the piston 23 is D and the length of one side of the piston 23 in the cylinder pore is L, then A = TTDL. 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 a function of (t is time). The velocity νθ is equal to the moving velocity V of the piston 23. If the pore 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, vO = B wsin (wt). As a result, equation (1) becomes the following equation.

F f =-z7TD L {Bpwsin (w t)} / s-(2)

In other words, the fluid friction force is proportional to the product of the Poivitch radius Bp, the piston diameter D, and the reciprocal of the gap s. The calorific value Q1 of the viscous heater per cylinder bore corresponds to the work performed on the fluid friction force Ff. (Q = nQl with n number of cylinder pores) Therefore, the calorific value Q is proportional to the fluid friction force F: H. Therefore, the heat generation Q is also proportional to the product of the pore 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 very small. The variation in the heating capacity for each heater is smaller than that of the conventional screw heater. In the viscous fluid of this embodiment, when the piston 23 (reciprocating member) reciprocates with the viscous fluid interposed between the cylinder bores (heating chambers) 12b and 13b, the fluid friction heat is reduced. appear. For this reason, even if the variation in the processing accuracy is the same as that of the conventional viscous whisk, the variation in the heating capacity is reduced. In addition, piston 23 is used as a reciprocating member. Biston is used in various devices, and its processing accuracy is generally high. Therefore, piston 23 used for viscous heater is relatively easy to process with high processing accuracy. Can be manufactured. Disconnection of piston 2 3 Because the surface is circular, it is easier to increase machining accuracy. Further, since the drive 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 with the drive shaft 20, a plurality of pistons 23 are formed. It can be driven in a relatively small space. As a result, the total surface area of the peripheral surface of the biston can be increased compared to a configuration in which one biston is provided in a housing of the same size. In addition, 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, is caused by the reciprocating motion of the piston 23 in the cylinder pore or the chamber 18. Replaced with viscous fluid. Therefore, since only a specific viscous fluid is not continuously subjected to a shearing action for a long time, deterioration of the viscous fluid due to excessive heat generation can be prevented. In addition, since the piston 23 is a double-headed type, the force acting on the swash plate 24 is balanced between the front and rear, and the durability is improved compared to a single-sided piston that has the same surface area on the peripheral surface of the piston. I do. The water jacket 27 is annular and formed long in the axial direction of the drive shaft 20, but circulating water is guided inside the water jacket 27 by spiral ridges 28a and 29a. Since the water circulates along the predetermined route, it is possible to reduce a short circuit and a stagnation of the flow path of the circulating water in the water jacket 27. For this reason, heat exchange from the viscous fluid in the cylinder pores 12b, 13b and the chamber 18 to the circulating water in the water jacket 27 can be performed efficiently. Since the ridges 28 a and 29 a are formed so as to project from the heat generating chamber side into the water jacket 27, the circulating water in the water jacket 27 and the heat generating chamber The contact area with the surrounding wall increases, and the heat exchange efficiency improves. Also, since the tips of the ridges 28a and 29a do not contact the opposing surface, heat is directly transmitted to the outside of the jacket 27 through the ridges 28a and 29a. And the efficiency of heat exchange with circulating water is improved. Further, since the water jacket 27 is formed not in a simple cylindrical shape but in a spiral shape along the peripheral surface of each of the cylinder pores 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 includes a cylinder block 39, a bottom plate 40 disposed below the cylinder block 39, and a top housing 41 disposed above the cylinder block 39, which are fastened by ports 42. The cylinder block port 39 is composed of an inner cylinder 39i and an outer cylinder 39o. A 0 ring 43a is interposed between the bottom plate 40 and the cylinder block 39, and a gasket 43b is interposed between the tube housing 41 and the cylinder block 39. . 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 pore 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. Cylinder hole 4 4 constitutes a heating chamber. The tob housing 41 has a support cylinder 41 a and a hole 41 b through which a crankshaft 46 as a drive shaft can be inserted. The crankshaft 46 has a support cylinder 41 a and a hole 41. The top housing 4 1 (rotatably supported via radial bearings 47, 48 fitted to b. One end of the crankshaft 4.6 protrudes from the support cylinder 41 a, It is operatively connected to the vehicle engine via a clutch (not shown) similar to the clutch.Rearing bearings with a live seal are used for radial pairings 47 and 48. The part 4 la is formed to have an inner diameter capable of passing through the crank part of the crankshaft 46. The piston 45 is formed in a cylindrical shape, and the piston shaft 49 is connected to the crankshaft 46 via a piston pin 49 and a connecting rod 50. The cylinder is reciprocated vertically with the rotation of the crankshaft 46. The viscous fluid contains almost half the volume of the cylinder block 39. The crankshaft 46, the piston pin 4 9 and connection The drive means is constituted by 50. A water jacket 51 is formed between the inner cylinder 39i and the outer cylinder 39o The outer cylinder 39o has a water inlet port. The water jacket 51 is formed as a cylindrical groove with the top housing 41 side open, and the water cylinder 51 has an inner cylinder 39 i. A helical guide ridge 54 protruding from the outer peripheral surface of the crankshaft 46 is provided in this embodiment. When rotated, the biston 45 is reciprocated via the connecting rod 50 and the biston bin 49 in a state in which a viscous fluid exists between the piston rod 45 and the peripheral surface of the cylinder bore 44. Shearing viscous fluid Friction force (fluid friction force) acts due, viscous fluid generates heat. Then, the heat is circulating water heat exchanger in the water jacket 5 1. In this embodiment, one biston 45 can provide a relatively large surface area that contributes to the fluid friction of the viscous fluid, and the structure is simplified. In addition, since the pistons 45 are formed in a cylindrical shape, that is, a shape in which the viscous fluid existing before and after in the moving direction of the piston can pass through the inside of the piston, the member that closes the end of the cylinder opening 39. (In this embodiment, it is not necessary to provide a housing portion for the viscous fluid in the bottom plate 40), which contributes to the miniaturization of the viscous fluid. In addition, the driving means of the piston 45 is disposed above the cylinder block 39, and the viscous fluid is contained in the cylinder block 39 in a portion corresponding to the movement range of the piston 45. Need not be increased unnecessarily.

(Third embodiment)

Next, a third embodiment will be described with reference to FIGS. In this embodiment, the piston is reciprocated by using a swash plate in the same manner as in the first embodiment. However, the difference is that the stroke of the piston can be changed and that the piston is a single-headed piston. It is different. As shown in FIG. 5, the front housing 55 is joined and fixed to the front ends of the cylinder port 56 and the outer rear housing 57 via a gasket 58. At the rear end of the cylinder block 56, an internal rear housing 59 is joined and fixed via a gasket 60 and a valve plate 61. The front housing 55, cylindrical dub 56, pulp plate 61, and inner housing 59 are fastened and fixed with Porto 15. Further, the front housing 55 and the external housing 57 are fastened and fixed by a port (not shown). The crankcase 62, which is a chamber for accommodating the swash plate, is The dub mouth is surrounded by 56. The drive shaft 20 is rotatably supported between the front housing 55 and the cylinder block 56 via a radial bearing 22 so as to cross the crankcase 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. The drive shaft 20 is connected to an external drive source (engine) (not shown) via an electromagnetic clutch. The substantially disk-shaped rotating support (lug plate) 64 is supported by the drive shaft 20 so as to be integrally rotatable in the crank chamber 62. 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) projecting from the rotation support 64 constitute a hinge mechanism. On the front side of the swash plate 65, a pair of guide bins 67 also constituting a hinge mechanism is protruded, and a spherical portion 67a provided at the tip of each guide pin 67 is provided with a support arm 6a. It is slidably fitted into a guide hole 6 6a provided in 6. That is, the swash plate 65 is non-rotatably connected to the rotary support 64 via the hinge mechanism. 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 linking the support arm 66 and the guide pin 67. The swash plate 65 is tilted by the slide guide relationship between the guide hole 66 a and the bulbous portion 67 a and the slide supporting action of the drive shaft 20. When the rotation center of the swash plate 65 is moved toward the cylinder block 56, the inclination angle (inclination angle) of the swash plate 65 is reduced. The coil spring 68 as a low-angle panel is wound around the drive shaft 20 between the rotary support 64 and the swash plate 65, and the coil spring 68 changes the swash plate 65 to a low angle. Bias in the direction. The ring-shaped stopper 6 9 is a swash plate 6 5 The minimum inclination angle of the swash plate 65 is defined by the swash plate 65 being fixed to the drive shaft 20 and the swash plate 65 abutting against the stopper 69. An inclination regulating protrusion 70 is integrally formed on the front side of the swash plate 65, and the maximum inclination angle of the swash plate 65 is defined by the inclination regulating protrusion 70 abutting on the rotary support 64. A plurality of cylinder bores 56 a are formed in the cylinder block 56 (only two are shown in FIG. 5), and the same number of single-headed pistons (hereinafter simply referred to as bistons) 71 are housed in the cylinder pores 56 a. ing. The swash plate 65 is engaged with the piston 71 via the shoe 26, and the rotational motion of the swash plate 65 is converted into the reciprocating motion of the piston 71. A champ 72 is formed between the valve plate 61 and the internal rear housing 59. In the valve plate 61, a suction hole 61a and a discharge hole 61b are formed at positions corresponding to the respective cylinder pores 56a. A suction valve 73 that opens and closes the suction hole 61a on the side of the cylinder bore 56a of the valve plate 61, and a discharge valve 74 that opens and closes the discharge hole 61b on the side of the champ 72 and a retainer 75 Are fixed by bolts 76 and nuts 77. Then, the viscous fluid in the chamber 72 is sucked into the cylinder pore 56 a via the suction hole 61 a and the suction valve 73 by the reciprocating operation of the piston 71. The viscous fluid that has flowed into the cylinder bore 56 a is discharged to the champ 72 through the discharge hole 61 b 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 78 a bearing a thrust load acting on the drive shaft 20 with the reciprocation of the piston 71 is interposed between the rotary support 64 and the inner wall surface of the front housing 55. A thrust bearing 78b is also provided in a housing formed at the center of the cylinder block 56. Between the outer peripheral surface of the cylinder port 56 and the outer surface of the inner housing 59 and the inner surface of the outer housing 57, a water jacket 79 as a heat radiating chamber is formed. A plurality of annular ridges 59 a are formed concentrically on the outer surface of the inner housing 59. A water inlet port 30 and a water outlet port 31 are formed on the outer peripheral portion of the outer housing 57. The crank chamber 62 is connected to pressure adjusting means 80 as swash plate angle changing means via a pipe 81. The end of the pipe 81 is connected to a hole formed in the front housing 55 through a sealing member (for example, an O-ring) 82 in an oil-tight manner. Are in communication. The pressure adjusting means 80 is a cylinder 83, a piston 84 slidably accommodated in the cylinder 83, an electric cylinder 85 for reciprocatingly driving the biston 84, and a control for controlling the electric cylinder 85. Device 86. An O-ring 84a for sealing is housed in a groove formed on the outer periphery of the piston 84. The electric cylinder 85 has a configuration in which a motor and a screw are combined to take out the rotational force of the motor as a linear thrust. For example, the rotor of the motor is hollow, and is disposed so that it cannot rotate and can move in the axial direction with a male screw as the output shaft 85a penetrating therethrough. The rotor is provided with a female screw screwed with the male screw. The control device 86 stores the relationship between the rotation speed and room temperature of the drive shaft 20 and the appropriate pressure in the crank chamber 62. Then, the controller 86 adjusts the pressure of the crank chamber 62 in accordance with the operation state such as the rotation speed of the drive shaft 20, the room temperature, and the like to control the amount of heat generation. The controller 86 adjusts the pressure so that the angle formed between the swash plate 65 and the drive shaft 20 becomes large when the viscous heater is started, that is, the angle of inclination becomes small. In this embodiment, machine oil is used as the viscous fluid, and the viscous fluid is used in the crankcase. 62, Champer 72, Cylinder bore 56A, Line 81 and Cylinder 83 are filled. As in the first embodiment, the viscous heater of this embodiment also generates heat by the reciprocation of the piston 71 via the swash plate 65 by the rotation of the drive shaft 20. The viscous fluid is compressed by the reciprocating motion of the piston 71, and the friction is generated by the viscous fluid friction in the side clearance between the piston 71 and the cylinder pore 56a. During the forward movement of the piston 71 toward the chamber 72, the viscous fluid is subjected to a compressive action, and the compressed viscous fluid presses and moves the discharge valve 74 to cause the discharge port 6 1b to move from the discharge hole 6 1b to the champ 7 2. Is discharged to Further, when the biston 71 returns, the viscous fluid in the chamber 72 pushes and moves the suction valve 73 to flow into the cylinder bore 56a. The theoretical calorific value Q of the viscous heater of this embodiment is expressed by the following equation.

Q = Vum p (heat generated by pressurization) + Ultimate heat due to viscous fluid friction in side clearance

Where [mm] is the differential pressure between the chamber 72 pressure and the discharge pressure, and V is the discharge amount. The stroke of the piston 71 changes depending on the inclination angle 0 of the swash plate 65. The greater the inclination angle 0, the greater the stroke, and the greater the amount of heat generated per rotation of the drive shaft 20. The inclination angle (9 of the swash plate 65 changes depending on the pressure in the crank chamber 62, and the inclination angle β decreases as the pressure in the crank chamber 62 increases, and the inclination angle (increases as the pressure decreases. 6 starts the viscous heater with the output shaft 85a of the electric cylinder 85 moved to the maximum protruding position, in which case the pressure in the crank chamber 62 is increased to the maximum pressure, as shown in FIG. The drive shaft 20 is rotated in a state where the inclination angle 0 of the swash plate 65 is minimized, and as a result, the stroke of the piston 71 is minimized, and Dynamic torque is reduced. Then, in order to increase the amount of heat generated when the drive shaft 20 rotates at a low speed, the controller 86 drives the electric cylinder 85 in the direction in which the output shaft 85a is immersed to reduce the pressure in the crank chamber 62. . As a result, the inclination angle 0 of the swash plate 65 changes through the intermediate state shown in FIG. 6 to the maximum position shown in FIG. Then, in the state shown in FIG. 5, the inclination angle 0 of the swash plate 65 becomes the maximum and the stroke of the piston 71 becomes the maximum, so that a necessary heat generation amount can be secured even at a low speed rotation. In addition, the control device 86 drives the electric cylinder 85 in the direction in which the output shaft 85a protrudes to increase the pressure in the crank chamber 62 in order to suppress excessive heat generation during high-speed rotation. As a result, when the inclination angle 0 of the swash plate 65 becomes small, the intermediate state shown in FIG. 6 is obtained. As the stroke of the piston 71 becomes small, the calorific value decreases. In this embodiment, since the swash plate angle changing means for changing the tilt angle の of the swash plate 65 is provided, by adjusting the tilt angle 0, it is possible to prevent an excessive amount of heat generation at high speed. The durability and reliability of the shaft sealing device 63 etc. are improved. Also, the required heat generation can be ensured even at low speed rotation. Furthermore, the swash plate angle changing means is configured to change the inclination angle 6> 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. It's easy. In addition, since the engine is started with a small inclination angle of 0, 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 start is performed smoothly. . In addition, since machine oil is used as a viscous fluid, lubrication of radial bearings 22 and 26, spherical parts 67a and thrust pairings 78a and 78b, etc. And the durability of each sliding part and bearing is improved. In addition, the controller 86 controls the operating conditions such as the rotation speed of the drive shaft 20 and room temperature.

The amount of heat generated is controlled by adjusting the pressure of the crank chamber 62 in accordance with the condition, so that an extra load is prevented from being applied to the drive source, and wasteful power consumption is reduced.

It should be noted that the embodiments are not limited to the above embodiments, but may 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 a piston driving means, a single-headed piston 71 is used instead of the double-headed piston 23 as shown in FIG. Configuration. In this case, the front cylinder block 12 of the viscous heater of the first embodiment is shortened, and the recess 11 a of the front housing 11 and the passage 19 of the cylinder block 12 are unnecessary. Become. A groove 71a is formed on the proximal end peripheral surface of the piston 71, so that a load is less likely to be applied to the proximal end surface of the piston 71 when the piston 71 moves. With this configuration, the screw force heater is smaller than that using a double-headed piston.

(2) In the first embodiment and the configuration of (1), as shown in FIGS. 9 (a) and (b), the pistons 23 and 71 have, as shown in FIGS. Form a passage 23 a, 7 lb communicating with 8. In this configuration, when the pistons 23, 71 move, the viscous fluid passes through the passages 23a, 71b, and the inside of the cylinder bores 12b, 13b and the chamber.

Move smoothly between 1 and 8. Therefore, if this configuration is adopted, it is not necessary to form the passage 19 in the cylinder blocks 12 and 13 and the front housing

Also, the concave portions 11a and 14a of the rear plate 11 and the rear plate 14 become unnecessary, so that the structure is simplified and the manufacturing cost can be reduced. (3) As shown in Figs. 10 (a) and (b), the distal ends of the pistons 23 and 71 are formed into a cylindrical shape, and the passages 23a and 7 lb are formed. The protrusions 87, 88 that can be inserted into the cylinder are formed so that there is a gap between the cylinder inner circumference and the gap between the piston outer circumference and the cylinder bore circumference. 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 bin 49 is connected to the piston 45. At a position away from the tip of the Then, an intermediate work 89 having a projection 89a inserted into the piston 45 is provided between the potato plate 40 and the cylinder block 39. A gap is formed between the peripheral surface of the projection 89a and the inner peripheral surface of the piston 45 so as to effectively generate heat generated by shearing. A cylindrical water jacket 90 independent of the water jacket 51 is formed in the intermediate block 89 so that the circulating water of the heating circuit flows through the water jacket 90 through an inlet port and an outlet port (not shown). I'm sorry. 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) The war evening jacket 90 may be omitted in (4). 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 the cam plate, a cam plate used in a wave cam type compressor disclosed in, for example, JP-A-7-97978, JP-A-7-189901, etc., is used. You may.

(7) Oscillating swash plate type (Pebble type) Similar to the compressor, the piston may be reciprocated using a swash plate that only oscillates with rotation restricted. (8) In the case of a configuration in which the piston is reciprocated via the swash plate, the thrust force applied to the swash plate and the drive shaft is small unlike the compressor, so that the thrust bearing 25 may be omitted. In this case, it is preferable to use angular bearings as the radial bearings 21 and 22.

(9) In the second embodiment, the crankshaft 46 may be disposed below the piston 45. That is, it is used in the same configuration as that of Fig. 4 and placed upside down. However, it is necessary to fill the viscous fluid into the room where the crankshaft 46 is housed and into the cylinder bore 44 of the cylinder block 39. Moreover, you may use it arrange | positioning horizontally.

(10) The cross-sectional shape of the cylinder bores 12b, 13b, and 44 should be other than circular, for example, triangular, square, hexagonal, elliptical, etc., and the outer shapes of the pistons 23, 45, 71 should be corresponding You may.

(1 1) Instead of the spiral ridges 28a, 29a, 54, ridges extending in parallel with the moving direction of the biston are provided in the zigzag jackets 27, 51 in a staggered manner. In this case, the production of the ridge becomes easy.

(12) Also, the ridges 28a, 29a, 54 may be formed such that their tips abut 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) Omit electromagnetic clutch 32, drive shaft 20 or crank The pulley 34 may be integrally rotatably supported on the shaft 46, and the driving force of the engine may be directly transmitted to the drive shaft via the pulley 34.

(15) As the radial bearing 21, a normal bearing may be used in place 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. Further, 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 that is wound around a pair of pulleys (mouths) housed in the housing and that reciprocates with the reciprocating rotation of the pulley may be used. The term "viscous fluid" as used herein means any medium that generates heat based on fluid friction under the shearing action of a "reciprocating member", such as a highly viscous liquid or semi-fluid. However, it is not limited to silicone oil. The “piston” is a member that reciprocates along a wall surface of a chamber (cylinder pore) that stores a viscous fluid, and is not limited to a so-called biston that moves in the same direction as the fluid in the room in a state where the chamber is partitioned. In addition, those that allow the fluid in the chamber to pass through the inside of the reciprocating member include, for example, cylindrical members (Biston) and those in which a hole that penetrates the piston in the axial direction is formed.

Claims

The scope of the claims

1. Heating chamber provided in the housing,

A reciprocating member disposed so as to be able to reciprocate with a viscous fluid interposed between the wall of the heating chamber and

Driving means for driving the reciprocating member,

A radiating chamber that is provided adjacent to the heat generating chamber and that exchanges heat generated by the reciprocating motion of the reciprocating member with a circulating fluid;

Reciprocating viscous heater equipped with.

2. The drive means transmits a rotational force of an external drive source, and

A cam plate that transmits reciprocating motion to the reciprocating member via a shoe as the drive shaft rotates.

2. The reciprocating viscous gear according to claim 1, comprising:

3. The reciprocating motion type according to claim 2, wherein the cam plate is a swash plate supported so as to be tiltable on the drive shaft, and provided with swash plate angle changing means for changing the tilt angle of the swash plate. Overnight viscous.

4. The swash plate is connected to a rotation support body rotatably supported by the drive shaft so as to be relatively non-rotatable via a hinge mechanism, and the swash plate angle changing means is provided in a chamber in which the swash plate is housed. 4. The reciprocating screw force heater according to claim 3, which is a pressure adjusting means that is in communication with the chamber and adjusts the pressure in the chamber.

5. The reciprocating screw screw 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.

-2 Z-

6. The reciprocating screw heater according to any one of claims 2 to 5, wherein a mechanical oil is used as the viscous fluid.

7. The reciprocating viscous heater according to any one of claims 1 to 6, wherein the reciprocating member is a piston.

8. The reciprocating viscous heater according to claim 1, wherein the driving means transmits a rotational force of an external driving source to the reciprocating member by a crank mechanism. .

9. The reciprocating screw force heater according to claim 8, wherein the reciprocating member is biston.

10. The reciprocating viscous heater according to claim 9, wherein the piston reciprocates below the crank mechanism, and the viscous fluid fills the moving range of the piston.

11. The reciprocating viscous filter according to any one of claims 7, 9 and 10, wherein a passage through which a viscous fluid can move inside the biston when the biston moves is formed.