JPH07198218A - Free piston type thermal gas engine - Google Patents

Abstract

PURPOSE:To improve durability by moderating vibration produced by unbalanced pistons of a thermal gas engine. CONSTITUTION:There are provided an operation gas enclosing casing 101, a high temperature side displacer 41H for dividing the casing 101 to a high temperature chamber 43, middle temperature chambers 44, 45, and a low temperature chamber 46, an operation gas heating high temperature side heat exchanger 111 disposed in a gas flow passage, a high temperature side regenerator 112, a middle temperature side heat exchanger 113, a low temperature side heat exchanger 114 disposed in the gas flow passage, and a low temperature side regenerator 115 and a middle temperature side heat exchanger 116. There are further provided a thermal gas engine where the displacers 41H and 41L are supported with springs 54, 55, an auxiliary cylinder for coupling the middle temperature chamber or a communication part gas flow passage, and a piston. The auxiliary piston is supported with a spring likewise the springs 41H and 41L, and a damper having a function as a balancer supported with a spring 64 is provided to reduce vibration.

Description

Detailed Description of the Invention

[0001]

The present invention relates to a low temperature heat source, a medium temperature heat source,
A free-piston hot-gas engine that operates between high-temperature heat sources and moves working gas to absorb heat from low-temperature heat sources and radiate heat to medium-temperature heat sources by the heat energy (thermal work) obtained from the high-temperature heat sources. Related to the improvement of.

[0002]

2. Description of the Related Art As a conventional hot gas engine, for example, JP-A-5-157385 and JP-A-5-157386 are known.
JP-A-5-157387 and JP-A-5-157387.
There is one as described in Japanese Patent No. 157388. The hot gas engine shown in these figures uses a crank mechanism as a means for reciprocating the high temperature side displacer and the low temperature side displacer. When such a crank mechanism is used, it is convenient because the phase and stroke of each displacer and auxiliary piston can be accurately specified, but on the other hand, a case for housing these mechanical parts is required. As a result, the size of the equipment is increased and the weight is increased, and the bearings of the crank mechanism and other parts that support the movement are burdened and their durability is reduced. Furthermore, in equipment using a crank mechanism, the imbalance of the reciprocating inertial force of each piston becomes a problem, and elimination of this inertial force is a difficult technology in terms of design. Usually, a method using a counterweight is adopted to solve this problem, but the case that can be solved by this method is limited to a specific case, and only the primary inertial force is targeted. Therefore, in reality, it is often considered how much imbalance is allowed, and vibration of the equipment cannot be eliminated, and the weight of the equipment increases by the weight of the counterweight. On the other hand, as a method for solving these mechanical problems, a configuration example in which each displacer is supported by a flexible body such as a spring is described in the following literature (1) to
It is described in (5).

(1) S. Schulz, "A Linear Model of a Fr
ee-Piston Vuillermier MachineCompared to Experimen
tal Result of a Prototype ", Proc. of the 27th Inter
national Conference of Energy Conversion, 1992 (2) S.Schulz, “Development of a Free Piston Vuill
eumier Machine for Cooling Purposes ", Proc. of the
5th International Stirling Engine Conference, 1990 (3) JPBudliger, “Stirling Heat Pump System with
Resonance Tube ", 6thInternational Stirling Engine
Conference, May 1993. Eindhoven, Netherland, p.25
-30 (4) Yoshinori Doi et al., “Heat Driven Heat Pump”, Japanese Patent Fair 5
-626 Publication (5) DMBerchowitz, “The Design, Development and P
erformance of a DuplexStirling Natural Gas Liquefi
er ", Proc. of the 17th International Conference of
Energy Conversion, 1982, p.1784-1789 FIG. 13 is a conceptual diagram showing the configuration of the device shown in the document (1), and the casing is not shown. In the figure, 1L is a low temperature side disperser, 1S is a mechanical spring for supporting it, 2H is a high temperature side dissipator, 2S is a mechanical spring for supporting it, 3a is a low temperature side heat exchanger,
3b is a low temperature side regenerator, 3c is a low temperature side medium temperature heat exchanger, 4a
Is a high temperature side heat exchanger, 4b is a high temperature side regenerator, 4c is a high temperature side medium temperature heat exchanger, and further the dispersers 1L and 2H.
The two are supported by gas springs 5.

FIG. 14 is a vertical sectional front view showing the configuration of the device shown in the reference (2). In FIG. 14, 6L is a low temperature side dissipator, 7H is a high temperature side dissipator,
8 is a heater, 9 is a heat exchanger, 10 is a regenerator, 11 is a water jacket, 12 is an outer jacket, 13 is a connecting rod,
14 is a starter. In this case, one display
The machine 6L is supported by the mechanical spring S1 for casing, and the displacers 6L and 7H are also supported by the mechanical spring S2. FIG. 15 is a conceptual diagram when two displacers of the device shown in Reference (3) are supported by a casing by mechanical springs, in which 15 is a casing and 16H is a high temperature. Side displacer, 17L is the low temperature side disperser, 16S and 17S are mechanical springs,
Reference numeral 18 is a resonance tube, 19 is a high temperature side regenerator, 20 is a high temperature side medium temperature heat exchanger, 21 is a low temperature side medium temperature heat exchanger, 22 is a low temperature side regenerator, and 23 is a low temperature side heat exchanger. As described above, three methods shown in FIGS. 13 to 15 can be considered as a method of supporting the two displacers in the casing by the flexible body.

FIG. 16 shows an embodiment found in Japanese Patent Publication No. 5-656 of Document (4).
24 is a case of a heat-driven heat pump, 25H and 2
5L is a high temperature side cylinder and a low temperature side cylinder respectively provided coaxially in the casing 24, and 26H and 26L are a high temperature side dissipator, a low temperature side dissipator, 27, respectively.
H, 27M and 27L are a high temperature room, a middle greenhouse and a low temperature room, respectively. 28H and 28L are high temperature side working gas flow paths and low temperature side working gas flow paths, 29H and 29L are high temperature side heat exchangers and low temperature side heat exchangers provided in the respective flow paths 28H and 28L, and 30H and 30L are respectively High temperature side regenerator and low temperature side regenerator, 31H and 31L are high temperature side medium temperature heat exchanger and low temperature side medium temperature heat exchanger, 32 is a partition wall integrated with casing 24, 32H and 32L are high temperature side and respectively The low temperature side displacer guides 33H and 33L are a high temperature side gas spring chamber and a low temperature side gas spring chamber, respectively, and each of these gas spring chambers 33H and 33L has a gas spring function. That is, the structure shown in FIG. 16 has substantially the same structure as that of FIG. 15, and it can be said that the flexible body is replaced with a gas spring from the mechanical spring.

FIG. 17 is shown in reference (5), FIG.
3 to 16 are partial sectional views of the equipment different in type from those shown in FIGS. 3 to 16. 26H is a high temperature side dissipator, 27L is a low temperature side dissipator, 28P is a power piston, 28a is Liquefaction heat exchanger, 28b is a low temperature side regenerator, 28c is a medium temperature side heat exchanger, 28d is an engine cooler, 28e is a high temperature side regenerator, and 28f is a heater. The two displacers 26H and 27L and the one power piston 28P are supported by gas springs (not shown), respectively. Further, a vibration isolator (not shown) is arranged below the hot gas engine so as not to transmit the vibration to the foundation.

[0007]

By the way, the above-mentioned prior art is simple in structure because it does not have a crank mechanism and is suitable for small size and light weight. However, it is suitable for balancing the inertial forces of the respective dispersers and power pistons. Is not considered,
Since the moving parts are coaxially arranged, the unbalanced inertial force is limited to the central axis. Therefore, in order to prevent the vibration due to the unbalanced inertial force from being transmitted to the foundation, it is common to employ a vibration damping device as shown in Reference 5. However, in such an antivibration device, vibration due to unbalanced inertial force is not transmitted to the foundation, but the load due to the above vibration is exerted throughout the operation of auxiliary equipment and piping attached to the equipment, and durability is not sufficient. Become. A hot gas engine (also referred to as a heat-driven heat pump) targeted by the present invention is a device that performs cooling and heating by using a high temperature heat source such as combustion as a driving source, and the greatest feature thereof is a gas (such as helium or helium) as a refrigerant. By using nitrogen, etc., it means not using CFCs at all. However, the power density (output per unit weight) is smaller than that of Rankine cycle refrigerators (evaporative refrigerators) that use CFCs as refrigerants, which are used for general air conditioning. Since this is larger and heavier than a general refrigerator, it is disadvantageous in terms of securing an installation space and cost when commercializing the refrigerator. In order to improve this point, a drive system using spring means has been proposed, but there is a problem in balance of inertial force, but since the mechanism is different from that of the conventional example described above, The anti-vibration device cannot be applied as it is. The present invention has been made in view of the above points, and an object thereof is to provide a small and lightweight free-piston type hot gas engine which is quiet and has high output density.

[0008]

The free-piston type hot gas engine of the present invention solves the above-mentioned problems by providing a casing in which a working gas is enclosed and a high temperature chamber inside the casing. A high-temperature-side displacer and a low-temperature-side disperser which are divided into a greenhouse and a low-temperature chamber, and a high-temperature-side heat exchanger and a high-temperature-side regenerator for heating a working gas, which are arranged in a gas passage connecting the high-temperature chamber and the middle greenhouse And a medium temperature side heat exchanger, a low temperature side heat exchanger arranged in a gas flow path connecting the low temperature chamber and the medium temperature chamber, a low temperature side regenerator and a medium temperature side heat exchanger, and two displacers are provided as spring means. A hot gas engine supported by the engine and an auxiliary cylinder and an auxiliary piston are added to this engine so as to be connected to the middle greenhouse or the gas passage of the communication part, and this auxiliary piston is connected to the above-mentioned high temperature side displacer and low temperature side displacer. Similarly if Supported by means, established a damper having a function as a balancer supported by the spring means is configured so as to reduce vibration of the equipment. In this case, further, a damping device may be provided in the spring means for supporting the damper, the damping coefficient of the damping device may be adjusted, or the spring constant of the spring means for supporting the damper may be adjusted. Deformation is possible.

[0009]

In the free-piston type hot-gas engine according to the present invention, the high-temperature side and low-temperature side dispersers and, in some cases, the auxiliary piston do not need to be mechanically driven from the outside, but have a variable pressure of the working gas. Force acting between the space kept at a constant pressure, flexible body acting on both displacers, friction acting on the displacer, and damping force caused by resistance when working gas flows through the flow path. Sustains vibration in a balanced state. Further, the engine causes a heat transfer due to the movement of the working gas and the temperature of each working space caused by the continuous vibration of each of the above-mentioned dissipators and pistons, and the vibration damping effect of the added damper enables quiet operation. . Further, various modifications such as providing a damping device in the spring means supporting the damper, adjusting the damping coefficient of the damping device, or adjusting the spring constant of the spring means supporting the damper are performed. If you do this,
Since the vibration absorbing action is adjusted to an appropriate level by such additional means, the heat engine can be operated more quietly.

[0010]

Embodiments of the present invention will be described below with reference to the drawings. In each of the embodiments, the corresponding parts are designated by the same reference numerals and the description thereof is omitted. (First Embodiment) A first embodiment of the present invention will be described with reference to FIG. In this embodiment, 101, 102 and 103
Each is a casing of a hot gas engine, and these are continuously integrated with each other by a method such as being connected by bolts or integrally molded. The high temperature side disperser 41H,
A low temperature side disperser 41L is provided so that the interior of the casing 101 is a high temperature chamber 43 and a medium greenhouse 44,4.
5, it is divided into a low temperature chamber 46 and a buffer chamber 42. A high temperature seal group 47 and a low temperature seal group 48 are respectively attached to the two dispersers 41H and 41L to guide their reciprocating motions and to seal the working gas inside, and a buffer is provided. In the chamber 42, a rod 49 connected to the high temperature dis- player 41H and a rod 50 connected to the low temperature dis- player respectively guide movements, and seal groups 51 and 52 for sealing each chamber are provided. It is attached. In the casing 102, a heater 111 for exchanging heat on the high temperature side, a high temperature side regenerator 112, and a high temperature side radiator 113 are also provided.
A cooler 11 for exchanging heat on the low temperature side is provided in the thing 103.
4, a low temperature side regenerator 115 and a low temperature side radiator 116 are provided respectively. Each chamber except the buffer chamber and the pipes are connected with bolts or integrally molded to form a working gas flow path 5
3 is formed.

The two displacers 41H and 41L are supported in the buffer chamber container integrated with the casing 101 by mechanical springs 54 and 55, which are examples of spring means in this figure. Is a gas spring,
Also, a combination of a mechanical spring and a gas spring may be used, and further, they may be provided on opposite sides, that is, in a high temperature chamber or a low temperature chamber. It is assumed that the two displacers are set so that the phase of the low temperature side disperser is delayed by about 90 degrees with respect to the high temperature side disperser by a spring means at a predetermined resonance frequency. The casing 61 of the vibration absorbing device 60 according to the present invention is integrally molded or bolted to the bottom of the casing 101. In the casing 61, a damper 62 having a predetermined mass (a damper having a predetermined mass md. In all the embodiments described below, the damper has a predetermined mass, this will be described below. (Not particularly described), and a guide 63 having a cushioning function for preventing the inner wall of the casing 61 from wearing due to metal contact with the casing 61 due to the reciprocal movement of the damper 62, and the damper 63. 62
And a mechanical spring 64 for supporting the. Although the mechanical spring 64 as the spring means is provided above the damper 62 in this figure, the effect does not change even if the mechanical spring 64 is provided below the damper 62. In addition, the damper 62 and the case
Instead of providing the guide 63 in order to avoid metal contact with the singing 61, a film of a resin containing a filler, for example, a resin such as PTFE may be formed on the inner surface of the casing 61. The casing 61 of the vibration absorber 60
Is for controlling the direction of the vibration absorbing action and for protecting the damper and the spring, and has a small hole 6 on the bottom wall or side wall thereof.
By forming 5a or 65b, the compression of gas in the casing can be prevented.

FIG. 2 schematically shows, as an analytical model, an example in which the spring means of the first embodiment is a combination of a mechanical spring and a gas spring, and two gas spring chambers are provided at the center of the casing. Is. In FIG. 2, the reference numerals for the main components related to the following analysis are attached with the reference numerals corresponding to those in FIG. 1, and the natural frequency of the vibration absorber is the case 1
It is designed by the following vibration analysis method using the multi-mass system vibration analysis technique so that the amplitude of 01 becomes 0 to the minimum.
Two dispersers 41H and 41L, a casing 101 for accommodating these dispersers, and a damper 62.
The equation of motion for is expressed by the following equations (1) to (4) using the respective symbols shown in FIG.

[0013]

[0014]

[0015]

[0016]

Further, it is assumed that the steady state caused by the external force is the harmonic motion represented by the following equations (5) to (8). xh = ahsin (ω ₀ t) (5) xc = acsin (ω ₀ t + φc) (6) xe = aesin (ω ₀ t + φe) (7) xd = adsin (ω ₀ t + φd) (8)

However, the symbols of the above equations are as follows. mh: High temperature displacer mass mc: Low temperature displacer mass me: Casing mass md: Dynamic damper mass Ch: High temperature displacer damping coefficient Cc: Low temperature displacer damping coefficient Ce: Case damping coefficient Cd: Dynamic damper damping coefficient Ah: High temperature rod area Ac: Low temperature rod area Pgh: High temperature gas spring chamber gas pressure Pgc: Low temperature gas spring chamber gas pressure P: Working chamber gas pressure Kh: High temperature side spring constant Kc: Low temperature side spring constant Kd: Damper spring constant xh: High temperature displacer displacement xc: Low temperature displacer displacement xe: Casing displacement xd: Damper mass displacement ah: High temperature displacer amplitude ac: Low temperature displacer amplitude ae: Casing amplitude ad: Damper amplitude φc: low temperature side piston phase (0 to −90 in the case of the present invention)
Φe: Case phase φd: Damper phase Then, in the present invention, the boundary condition is xe = 0 (that is, the non-damping damper Cd is 0) or the minimum (that is, the damping damper is Cd = 0).
Other than that, each numerical value will be determined by the above equations (1) to (8). Formula (1) and Formula (2) above
External forces Ah (Pgh-P) and Ac (Pgc-P) can be obtained by inserting a rod into the gas spring chamber or into the buffer chamber to obtain the differential pressure between the gas spring chamber or the buffer chamber and the working chamber. .

(Second Embodiment) Next, a second embodiment of the present invention will be described with reference to FIG. Reference numeral 70 denotes an auxiliary cylinder means for guiding the reciprocating movement of the auxiliary piston 72 and a mechanical spring 71 or other spring means for supporting the auxiliary piston 72 in the auxiliary casing 104, and an upper auxiliary working chamber 73. , A group of seals 75 for keeping the lower auxiliary working chamber 74 airtight. The upper auxiliary working chamber 73 and the working gas flow passage 76 are connected by pipes or integrally formed by working gas flow passage 53 to communicate with each other, and the lower auxiliary working chamber 74 and the buffer chamber 42 are formed by piping or integrally formed in the gas flow passage. They are connected by 77 and communicate with each other. In the present embodiment, the three mechanical springs 54, 55 and 71 have a high temperature side display at a predetermined resonance frequency.
The phase of the low temperature side disperser 41L with respect to the high temperature side disperser 41H is delayed by about 0 degree or about 180 degrees with respect to the high temperature side disperser 41H.
When the phase delay of L is about 0 degree, the phase of the auxiliary piston 72 with respect to the high temperature side disperser 41H is from 0 degree to 18 degrees.
0 degree delay or high temperature side disperser 41
The phase of the low temperature side disperser 41L with respect to H is about 90.
If the delay is delayed, the phase of the auxiliary piston 72 with respect to the high temperature side disperser 41H is set to be delayed from 90 degrees to 180 degrees.

The two displacers 41H and 41L are mechanical springs 54 and 55 which are examples of spring means in this embodiment.
It is supported by a buffer chamber container integrated with casing 101, but these mechanical springs may be gas springs or a combination of mechanical springs and gas springs. Further, it may be changed so as to be provided on the opposite side, that is, in the high temperature chamber or the low temperature chamber. A casing 61 of the vibration absorbing device 60 according to the present invention is fixed to the bottom of the casing 101. Since the structure of the vibration absorbing device 60 is the same as the structure of the vibration absorbing device 60 described in the first embodiment, the description thereof will be omitted. FIG. 4 schematically shows the second embodiment as an analytical model. The natural frequency of the vibration absorber is designed by the following vibration analysis method using the multi-mass system vibration analysis technique so that the amplitude of the casing 101 becomes 0 to minimum. The equations of motion for the two displacers, the auxiliary piston, the casing accommodating the displacer, and the damper are given by the equations (1), (2) and (4), and the following equation (9). The result is as shown in Expression (10).

[0021]

[0022]

Further, it is assumed that the steady state caused by the external force is the harmonic motion represented by the above equations (5) to (8). However, although the symbols of the above equations are the same as those shown in equations (1) to (8), the first ones are as follows. mp: auxiliary piston mass Cp: auxiliary piston damping coefficient Ap: auxiliary cylinder area Pgp: auxiliary buffer chamber gas pressure Kp: auxiliary spring constant xp: auxiliary piston displacement ap: auxiliary piston amplitude φp: auxiliary piston phase Each number will be decided. The boundary condition is the same as the above condition.

(Third Embodiment) Next, a third embodiment of the present invention will be described with reference to FIG. The present embodiment is an improvement of the first embodiment (FIG. 1), so that the stress acting on the mechanical spring in the casing 61 of the vibration absorbing device 80 does not result in both-side torsion, and the damper 62 is neutral. Mechanical springs 81 and 82 are provided on both upper and lower sides of the damper 62 so that the points can be regulated, and the same vibration absorbing device can be applied to the hot gas engine of the second embodiment (FIG. 3). is there. (Fourth Embodiment) Next, a fourth embodiment of the present invention will be described with reference to FIG. In the case of this embodiment, the case of the vibration absorbing device 85 is
A characteristic is that a gas spring 84 is used in place of the mechanical spring according to the first embodiment as the spring means for supporting the damper 62 in the sing 83, and a similar vibration absorbing device is used in the second embodiment (FIG. 3).
It is also applicable to the hot gas engine of. (Fifth Embodiment) Next, a fifth embodiment of the present invention will be described with reference to FIG. In the case of the present embodiment, the damper 6 is attached to the spring means for supporting the damper 62 in the casing 83 of the vibration absorbing device 90.
The mechanical springs 86a and 86b provided on both the upper and lower sides of the second gas generator 2 and the gas spring 84 are used in combination, whereby the stress applied to the mechanical spring can be reduced.
The same vibration absorbing device can be applied to the hot gas engine of the second embodiment (FIG. 3).

(Sixth Embodiment) Next, a sixth embodiment of the present invention will be described with reference to FIG. The structure of the vibration absorbing device 95 of this embodiment is similar to that of the vibration absorbing device 80 of the third embodiment (FIG. 5), but a damper supported by mechanical springs 81 and 82 in a closed casing 99. Upper damper chamber 8 at 87
8. A through hole 91 having a relatively small diameter for communicating the lower damper chamber 89 is provided, and a viscous liquid such as turbine oil or a high pressure gas is enclosed in a space inside the casing including the through hole 91. However, the function as a viscous damping device is added. As a result, the vibration of the casing 101 cannot be completely eliminated, but the vibration can be considerably reduced and a damping effect in a wide range can be expected. This vibration absorbing device is also applicable to the hot gas engine of the second embodiment.
At this time, the casing 99 is cooled and the temperature of the liquid is lowered to improve the durability. (Seventh Embodiment) Next, a seventh embodiment of the present invention will be described with reference to FIG. This figure (A) shows the structure for adjusting the damping coefficient by connecting the external pipes 92A and 92B to the vibration absorbing device 100A. In this figure (B), a part of the casing 97 of the vibration absorbing device 100B is thickened. A mechanism for adjusting the damping coefficient is provided inside the meat. In FIG.
Reference numeral 3 is a closed casing, and a damper 62 having no through hole therein and mechanical springs 81, 8 above and below the damper 62.
2 and a group of seals 63 attached to the damper 62 are provided, and a casing 93 is provided in an upper damper chamber 88 and a lower damper chamber 89 defined by the damper 62 in the casing 93.
External pipes 92A and 92B are connected through the side wall of
The other ends of the two external pipes 92A and 92B are connected to a needle valve 94, respectively, and these are connected in a loop to form a dashpot. The needle valve 94 may be replaced with a valve with an actuator. The damping coefficient of the vibration absorber can be adjusted statically or dynamically by adjusting the operating portion 94A of the needle valve 94 or setting the operating circuit of the valve with an actuator. The figure (B) is the external piping 92A, 92B of the figure (A).
This is an example in which the gas passage 98 is provided in the thick portion of the casing 97 without using the casing, and is built in the casing structure including the needle valve 94. . Also in this case, a valve with an actuator can be provided instead of the needle valve 94. The operation and effect are the same as in the case of FIG. Also in the case of the seventh embodiment, these vibration absorbing devices can be applied to the hot gas engine of the second embodiment.

(Eighth Embodiment) Next, an eighth embodiment of the present invention will be described with reference to FIG. In this embodiment, the spring constant of the gas spring 84 shown in FIG. 7 can be adjusted, and a part of the gas spring chamber 121 functioning as a gas spring can be used as a piston 122 to change its position. The spring constant of the gas spring (121) is the ideal gas or polytro
The rate of change of the volume of the gas spring chamber due to the displacement of the damper mass is a parameter for determining the spring constant, but the gas mass in the gas spring chamber increases and decreases as the volume of the gas spring chamber increases and decreases. There must be. If this mass change does not occur, the neutral point of the damper will move and the spring constant cannot be expected to change. In order to avoid this movement of the neutral point, it is necessary to place gas springs of the same performance in opposition to the damper mass, or to secure the neutral point with something other than a gas spring.

In the fifth and fifth embodiments of the present invention, the neutral points are secured by the two mechanical springs 86a and 86b, respectively.
In the vibration absorbing device 110 of this embodiment, the piston 122 forming a part of the wall of the gas spring chamber 121 is driven by the driving device 123 via the hydraulic chamber 124. The drive unit 123 is controlled by the control unit 126 so as to automatically minimize the vibration detected by the sensor 125 fixed to the side wall of the casing 101 via the actuator 127A or 127B. The adjustment of the gas in the gas spring chamber 121, which has become insufficient due to the adjustment of the volume in the gas spring chamber 121, is performed by the inflow and outflow of the gas through the gap of the seal 129 provided on the damper rod 128 attached to the damper 62. It is also possible by means of gas flow in and out by a pipe 134 connected to small holes 133a to 133c provided through the side walls of the buffer chamber 42, the upper and lower damper chambers 131 and 132, and the gas spring chamber 121, respectively. Is. It is also possible to control the amount of gas passing through each small hole by providing a valve 135 in the middle of the pipe 134 as shown in the figure. By combining this embodiment and the seventh embodiment, it is possible to provide an optimum vibration absorbing action even during operation. In the present embodiment, the spring constant of the gas spring is automatically adjusted by the control device and the actuator, but these are removed and a driving tool such as a screw mechanism is provided at the bottom of the driving device 123 and manually operated. It is also possible to adjust the spring constant. The spring constant adjusting mechanism according to the present embodiment can be applied to the hot gas engine according to the second embodiment.

(Ninth Embodiment) Next, a ninth embodiment of the present invention will be described with reference to FIG. In the present embodiment, a magnet (not shown) is fixed to the damper 141 of the vibration absorbing device 120, an electromagnetic coil 143 is arranged around the casing 142, and the damper 141 is electromagnetically controlled. is there. The damper 141 can be vibrated by energizing the electromagnetic coil at the time of starting the hot gas engine. However, in this state, the vibration absorbing action is reversed, so the energization is performed at the frequency at which the casing 101 vibrates most. To do. The figure shows an example in which the damper 141 of the absorber 120 is supported by the mechanical springs 81 and 82, but another embodiment of the present invention in which the damper mass is supported by a gas spring or by using both a mechanical spring and a gas spring. This embodiment can be additionally applied to the above. This electromagnetic control mechanism can also be applied to the hot gas engine of the second embodiment of the present invention. (Tenth Embodiment) Next, referring to FIG. 12, a first embodiment of the present invention will be described.
Example 0 will be described. A vibration absorbing device 140 of the same figure shows a comprehensive vibration absorbing device of a hot gas engine which is combined in order to make the best use of the advantages of the seventh, eighth and ninth embodiments. It is a thing. Therefore, the reference numerals of the corresponding components are shown with the reference numerals used in the respective drawings except for the needle valve 96 and its operating portion 96A. The vibration absorbing device 140 can also be applied to the hot gas engine of the second embodiment of the present invention.

[0029]

As described above, the present invention is a free-piston type hot gas engine equipped with a damper supported in a required configuration for driving a displacer and an auxiliary piston by utilizing resonance of a vibration system. Therefore, it has the following excellent effects. The structure is simple, mechanical friction loss due to the crank mechanism, etc. can be reduced, and high performance can be expected. Since it has a high output density and can be made smaller and lighter, it is possible to conserve resources and perform cooling and heating without using CFCs. By the vibration absorbing action of the added damper, it is possible to provide a device that is quiet and has high durability of the accessory parts. Furthermore, a damping device is provided in the spring means that supports the damper, and the damping coefficient of this damping device can be adjusted.
Alternatively, if various modifications are made such that the spring constant of the spring means supporting the damper can be adjusted, the vibration absorbing action is adjusted to an appropriate one by such additional means, so that the heat engine is further improved. You can drive quietly.

[Brief description of drawings]

FIG. 1 is a schematic cross-sectional view showing the configuration of a hot gas engine equipped with a vibration absorbing device, showing a first embodiment of the present invention.

FIG. 2 is a diagram schematically illustrating an analysis model in the first embodiment of the present invention.

FIG. 3 is a diagram showing a second embodiment of the present invention and is a schematic sectional view showing the configuration of a hot gas engine provided with a vibration absorbing device.

FIG. 4 is a diagram showing a second embodiment of the present invention and is a diagram schematically showing an analysis model.

FIG. 5 is a schematic cross-sectional view showing a configuration of a hot gas engine equipped with a vibration absorbing device in a view showing a third embodiment of the present invention.

FIG. 6 is a schematic cross-sectional view showing the configuration of a hot gas engine equipped with a vibration absorbing device, showing a fourth embodiment of the present invention.

FIG. 7 is a diagram showing a fifth embodiment of the present invention and is a schematic sectional view showing the configuration of a hot gas engine provided with a vibration absorbing device.

FIG. 8 is a diagram showing a sixth embodiment of the present invention and is a schematic sectional view showing the configuration of a hot gas engine provided with a vibration absorbing device.

FIG. 9 is a diagram showing a seventh embodiment of the present invention and is a schematic sectional view showing the configuration of a hot gas engine provided with a vibration absorbing device.

FIG. 10 is a diagram showing an eighth embodiment of the present invention and is a schematic sectional view showing the configuration of a hot gas engine provided with a vibration absorbing device.

FIG. 11 is a schematic cross-sectional view showing the configuration of a hot gas engine equipped with a vibration absorbing device, showing a ninth embodiment of the present invention.

FIG. 12 is a diagram showing a tenth embodiment of the present invention and is a schematic sectional view showing the configuration of a hot gas engine provided with a vibration absorbing device.

FIG. 13 is a diagram showing a conventional example, which is a conceptual diagram showing a configuration of a hot gas engine.

FIG. 14 is a vertical sectional front view showing a configuration of a hot gas engine showing a conventional example.

FIG. 15 is a diagram showing a conventional example, which is a conceptual diagram showing a configuration of a hot gas engine.

FIG. 16 is a diagram showing a conventional example, which is a conceptual diagram showing a configuration of a hot gas engine.

FIG. 17 is a partial cross-sectional view showing the configuration of a hot gas engine showing a conventional example.

[Explanation of symbols]

41L: low temperature side displacer 41H: high temperature side displacer 43: high temperature chamber 44, 45: middle greenhouse 46: low temperature chamber 54, 55, 64, 71, 81, 82, 86a, 86
b: spring means (mechanical spring) 60, 80, 85, 90, 95, 100A, 100B,
110, 120, 140: Vibration absorber 62, 87, 141: Damper 72: Auxiliary piston 84, 121: Spring means (gas spring) 94: Needle valve (valve with actuator) 101-103: Casing 104 : Auxiliary casing 123: Driving device 125: Sensor 126: Control device 127A, 127B: Actuator 143: Electromagnetic coil

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Fusao Terada 2-5-5 Keihan Hondori, Moriguchi City, Osaka Sanyo Electric Co., Ltd.

Claims (7)

[Claims] 1. A casing in which a working gas is enclosed, and a high temperature side disperser and a low temperature side disperser which divide the inside of the casing into a high temperature chamber, a middle greenhouse and a low temperature chamber.
A high temperature side heat exchanger, a high temperature side regenerator and a medium temperature side heat exchanger for heating the working gas arranged in the gas flow path connecting the high greenhouse and the middle greenhouse, and a gas flow path connecting the low temperature room and the middle greenhouse. In a free-piston type hot gas engine having a low temperature side heat exchanger, a low temperature side regenerator and an intermediate temperature side heat exchanger, and each of the above displacers supported by spring means, a damper supported by spring means is added. A free-piston type hot gas engine characterized by the above. 2. A casing in which a working gas is enclosed, and a high temperature side disperser and a low temperature side disperser which divide the inside of the casing into a high temperature chamber, a medium greenhouse and a low temperature chamber,
A high temperature side heat exchanger, a high temperature side regenerator and a medium temperature side heat exchanger for heating the working gas arranged in the gas flow path connecting the high greenhouse and the middle greenhouse, and a gas flow path connecting the low temperature room and the middle greenhouse. A low temperature side heat exchanger, a low temperature side regenerator and a medium temperature side heat exchanger, and an auxiliary cylinder and an auxiliary piston so as to be connected to the middle greenhouse or the gas passage of the communication part. A free-piston type hot gas engine in which a damper supported by spring means is added to a free-piston type hot gas engine in which a spring and a low temperature side displacer are supported by spring means. 3. The free-piston type hot gas engine according to claim 1 or 2, wherein a spring device for supporting the added damper is provided with a damping device. . 4. The free-piston type hot gas engine according to claim 1 or 2, wherein a spring means for supporting the added damper is provided with a damping device having a mechanism capable of adjusting a damping coefficient and a control circuit. A free feature that is equipped with a function to minimize the vibration of the engine even during operation.
Piston type hot gas engine. 5. The free piston type hot gas engine according to claim 1 or 2, further comprising a mechanism for adjusting a spring constant of spring means for supporting the added damper. Type hot gas engine. 6. The free-piston type hot gas engine according to claim 1 or 2, further comprising a spring unit having a mechanism and a control circuit for adjusting a spring constant of a spring unit supporting the added damper, and operating. A free-piston type hot gas engine, which is characterized by having a function of adjusting the vibration of the engine to a minimum even at times. 7. The free-piston type hot gas engine according to claim 1, wherein the added damper is used as a balancer, and a magnet is added to the damper by an electromagnetic coil. A free-piston type hot gas engine characterized by being used as a starting device by being driven.