JP2009052866A - Cold storage type refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cold storage type refrigerator achieving stable operation for a long period, stable refrigerating capability and high cooling efficiency by improving the operation of a vibration source which causes the reciprocating motion of a displacer provided on the cooling part of the cold storage type refrigerator. <P>SOLUTION: The cold storage type refrigerator 1 comprises the vibration source 40 for causing the reciprocating motion of the displacer 37, a supporting member 43 having a rod 42 and stored in a case 41 of the vibration source 40, first bearings 44, 45 and second bearings 46, 47 having rotatable guides and disposed between each of the faces of the supporting member 43 and each of inner faces 41a, 41b of the case 41, and coil springs 48, 49 disposed between each of the first bearings 44, 45 and each of the second bearings 46, 47. The coil springs 48, 49 are mounted at their ends on cylindrical portions 44b, 45b, 46b, 47b of the bearings 44, 45, 46, 47. The spring force of the coil springs 48, 49 operates on the displacer 37 in the direction of its center axis A. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a regenerative refrigerator that generates refrigeration using a regenerator such as a Stirling refrigerator or a pulse tube refrigerator.

  A conventional regenerative refrigerator includes a compression suction unit that compresses and sucks working gas by a movable part of a linear motor that reciprocates on an axial straight line, and a cooling unit that expands the compressed working gas and generates refrigeration. The compression suction part has L-shaped ring washers (copper plated with gold) on both sides of a spring receiving part (material, polyimide resin of insulating material) provided at the peripheral tip of the movable part. The compression coil springs are arranged opposite to each other with a ring washer, the compression coil spring is maintained in a compressed state in the movable range of the movable part, and the ring washer and the compression coil spring are energized to energize the movable coil of the linear motor. Connected to each other. The cooling unit has a pair of compression springs opposed to the spring seats on both sides of the movable unit that reciprocally moves on the straight line in the axial direction by supplying or sucking the working gas in the compression and suction unit, and the compression coil spring is moved to the movable unit. (See, for example, Patent Document 1).

  Also, a Stirling cooler including a movable part of a linear motor that reciprocally moves on an axial straight line and a compression / suction part for working gas by the movable part, provided on both surfaces of the movable part on the back end side of the piston A pair of compression coil springs are disposed between the receiving part, a spring receiving washer fixed to the main body, and a bottom surface of the cylindrical part of the main body, and the pair of compression coil springs are arranged in directions opposite to each other in winding direction ( For example, Patent Document 2).

  Further, the compressor includes a piston driven by a linear motor, and includes a first spring fixing support member, a second spring fixing support member, which are fixedly coupled to both surfaces of a disk at a piston end, A first spring support member fixedly coupled to the cover facing the spring fixing support member, and a second spring support member fixedly coupled to the end surface of the inner laminated core facing the second spring fixing support member A first spring interposed between the first spring fixing support member and the first spring supporting support member, and a second spring interposed between the second spring fixing support member and the second spring supporting support member. And is configured. One ends of the first spring and the second spring are loosely supported by the first spring support member, the second spring, and the second spring support member, respectively. The other ends of the first spring and the second spring are engaged with and fixed to the edges of the first spring fixing support member and the second spring fixing support member. (For example, patent document 3).

In addition, a piston in which a piston head, a linear motor armature, and a guide piston are coupled with a bolt, a cylinder in which the piston slides, a piston guide in which the guide piston slides, and a linear motor disposed outside the cylinder A linear compressor including a stator, wherein a pair of springs are mounted oppositely to a cylindrical portion of an inner end surface of a guide piston and a cylindrical portion of a spring support fixed to the end portion of the piston guide, A washer having a sliding bearing function is interposed between the opposed end surfaces, and the inner diameters of the end portions of the respective springs are attached to both cylindrical portions of the support member (for example, Patent Document 4).
JP 2004-12080 A JP 2003-185283 A Japanese Patent No. 3058413 US005727932A

  However, according to Patent Document 1, in the cooling unit, the end surfaces of the pair of compression springs arranged on the spring seats on both sides of the movable unit are the torsional force (circumferential force) of the spring generated by the contraction and relaxation of the spring. As a result, the seat surface of the spring seat is slid and slid to cause a scratch on the seat surface of the spring seat, and at this time, wear powder is generated. Similarly, the end face on the opposite side of the compression spring swings and slides on the spring receiving seat of the spring receiving sleeve and the spring receiving seat of the main body to cause a sliding scratch on the spring receiving seat, At that time, abrasion powder is generated. There is a problem that these abrasion powders are caught in sliding portions of each part, causing a failure of the refrigerator, a decrease in efficiency due to an increase in mechanical loss, or a decrease in refrigerating capacity due to a decrease in piston amplitude.

  In the compression suction portion, one end face of the compression coil spring provided on the movable portion of the linear motor is provided on an L-shaped ring washer fitted on both sides of the spring receiving portion on the movable portion side of the linear motor. In the L-shaped ring washer, a lead wire for energization is connected to the coil of the linear motor via a compression coil spring, and the ring washer must be fixed so as not to move in order to prevent disconnection of the lead wire. Therefore, due to the torsional force due to the contraction and relaxation of the spring, the compression coil spring swings and slides on the ring washer surface in the same manner as the cooling part described above, causing the ring washer to slide and wear. Powder is generated. The other end face of the compression coil spring is also provided on an L-shaped first ring washer (copper material is gold-plated) fitted into an insulating seat provided on the main body. The lead wire of the coil of the linear motor is connected to the first ring washer, and the first ring washer must be fixed so as not to move in order to prevent disconnection of the lead wire. Accordingly, wear powder is generated in the same manner from the first ring washer. As described above, these wear powders have a problem of causing a failure of a refrigerator, a reduction in efficiency due to an increase in mechanical loss, or a reduction in refrigerating capacity due to a decrease in piston amplitude.

  According to Patent Document 2, the spring receiving portion on the movable portion side receives a torsional force from the end surfaces on the opposed surface side of the pair of compression coil springs, but the pair of compression coil springs are arranged in directions opposite to each other in winding direction. Therefore, the torsional forces cancel each other, the compression coil spring and the spring receiving portion do not move relative to each other, and no wear powder is generated. However, the other end surface of the compression coil spring swings and slides on the seat surface of the spring receiving portion due to the torsional force of the compression coil spring, and causes a sliding scratch on the seat surface of the spring receiving portion. At that time, abrasion powder is generated, and there is the same problem as described above.

According to Patent Document 3, when the first spring and the second spring contract and relax, the first spring fixing support member, the first spring on the side fixed to the second spring fixing support member, The end portions of the two springs do not move with respect to the first spring fixing support member and the second spring fixing support member, and no abrasion powder is generated. However, the first spring support member, the first spring gently supported by the second spring support member, and the end of the second spring are supported by the torsional force of each spring. The first spring support member and the second spring support member are slidably slid relative to the second spring support member. I have the same problem.

  According to Patent Document 4, the support member is supported by a pair of springs with a washer interposed therebetween. Since the spring has bending rigidity, the vibration system is determined by the mass of the support member and the bending rigidity of the spring. There is a risk that the support member swings in a direction orthogonal to the sliding direction of the piston. Due to the lateral swing, the spring shaft is twisted, and the piston head and the guide piston slide while sliding against the sliding surface, which causes a problem of an increase in mechanical loss and a decrease in the amplitude of the piston head.

  The present invention has been made in view of the above-described problems, and suppresses generation of wear powder and mechanical loss, and improves the operation of a vibration source that causes reciprocation of a displacer provided in a cooling unit of a regenerative refrigerator. Thus, an object of the present invention is to provide a regenerative refrigerator that can be stably operated for a long period of time, has a stable refrigeration capacity, and has a high cooling efficiency.

  In order to solve the above-mentioned problems, the invention described in claim 1 includes a compression space that compresses the working gas, a radiator that radiates heat of the working gas compressed in the compression space, and a working gas that reciprocates and flows through the radiator. A regenerative refrigerator that includes a regenerator that exchanges heat with, a expansion space provided with a displacer that expands the working gas cooled by the regenerator, and a vibration source that causes reciprocation of the displacer, The vibration source includes a case through which a rod positioned on the central axis of the displacer passes, a support member housed in the case and provided with the rod, and a first slide provided with a rotatable guide provided on both sides of the support member and rotatable. A moving member, a second sliding member provided on both inner surfaces of the case and provided with a rotatable guide, a coil spring disposed between the first sliding member and the second sliding member, and a coil spring mounted To the displacer Guide portion for directing the central axis direction of the spring force of the coil spring that includes a city.

  According to a second aspect of the present invention, the vibration source is disposed on a fixing member located on the opposite side of the rear face of the displacer, and connects the rod to the rear face of the displacer.

  According to a third aspect of the present invention, the vibration source is disposed in the displacer, and the rod is connected to a connecting member facing the side through which the rod passes from the vibration source.

  According to a fourth aspect of the present invention, the guide portion is disposed on at least one of the first sliding member and the second sliding member.

  According to a fifth aspect of the present invention, the guide portion is disposed on the inner periphery of the first sliding member and the second sliding member.

  In the invention according to claim 6, the guide portion is a cylinder.

  According to the first aspect of the present invention, the vibration source that causes the reciprocation of the displacer includes a support member housed in a case and provided with a rod, and a rotation guide provided on both sides of the support member and rotatable. Coil springs are respectively provided between the sliding member and the second sliding member provided on both inner surfaces of the case and provided with a rotatable guide. Accordingly, the torsional force generated by the contraction and relaxation of the coil spring acts on the first sliding member and the second sliding member provided at both ends of the coil spring. The frictional force between the end surface of the coil spring and the first sliding member is greater than the frictional force between the first sliding member and the support member, and the friction between the end surface of the coil spring and the second sliding member. Since the force is larger than the frictional force between the second sliding member and the inner surface of the case, the end surface of the coil spring does not slide with respect to each sliding member, and the supporting member and the case which are the mating surfaces of each sliding member Oscillates and slides on the inner surface. As a result, there is no generation of abrasion powder due to biting of the coil spring end face of the prior art into the sliding surface, and it is possible to provide a regenerative refrigerator with high cooling efficiency, stable operation for a long period of time, stable refrigerating capacity.

  In addition, the vibration source includes a guide portion that is attached to the coil spring and directs the direction of the spring force (compression force) of the coil spring acting on the displacer toward the center axis of the displacer. Acts on the axis of the rod and the central axis of the displacer. Therefore, the moment due to the spring force of the coil spring contraction and relaxation does not act on the displacer and the rod, the displacer and the rod reciprocate smoothly, the mechanical loss due to the conventional twisting is reduced, and the displacement of the displacer increases. To do. As a result, the refrigeration capacity is stabilized and the cooling efficiency is increased.

  According to the second aspect of the present invention, the vibration source is disposed on a fixing member located on the opposite side of the displacer rear surface so that the shaft is located on the central axis of the displacer, and the rod is connected to the rear surface of the displacer. Therefore, it acts in the same manner as in claim 1 and produces the same effect.

  According to a third aspect of the present invention, the vibration source is provided in the displacer, and the rod is arranged so that the shaft is positioned on the central axis of the displacer on the connecting member facing the side through which the rod passes from the vibration source. Since it connects, it acts like Claim 1, produces the same effect, the axial length of a cooling part becomes short, and a cooling part can be reduced in size.

  In the invention according to claim 4, since the guide portion is disposed on at least one of the first sliding member and the second sliding member, the spring force due to the contraction and relaxation of the coil spring is not affected by the shaft of the rod and the displacer. Acting on the central axis of Therefore, the moment due to the spring force of contraction or relaxation of the coil spring does not act on the displacer or the rod, and the displacer or the rod reciprocates smoothly, the mechanical loss is reduced, and the amplitude of the displacer is increased. As a result, the refrigeration capacity is stabilized and the cooling efficiency is increased.

  In the invention according to claim 5, the guide portion is arranged on the inner periphery of the first sliding member and the second sliding member, and the inner diameter side of the coil spring is provided with a slight gap with respect to the outer peripheral surface of the guide portion. Installing. When the coil spring contracts, the inner diameter of the coil spring can be expanded without restriction, the axial twist of the conventional coil spring does not occur, the displacer or the rod reciprocates smoothly, the mechanical loss is reduced, and the displacer amplitude is increased. Increase. As a result, the refrigeration capacity is stabilized and the cooling efficiency is increased.

  In the invention according to claim 6, since the guide portion is cylindrical and has a simple shape, the cost of the first sliding member and the second sliding member is reduced.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

(Example 1)
FIG. 1 is a sectional view of a regenerative refrigerator according to the present invention. The regenerative refrigerator 1 is configured by connecting the compression unit 2 and the cooling unit 30 to the flow path holes 4a and 4b provided in each through the pipe 4, and is filled with helium (working gas) as the working gas. A Stirling refrigerator 1 (cool storage type refrigerator) is formed.

  The compression unit 2 includes a compression cylinder 5, stators 11 and 21 of a pair of linear motors 10 and 20 fixed at symmetrical positions with respect to a flow path hole 4 a provided on the outer peripheral surface of the compression cylinder 5, It is formed from movable bodies 12 and 22 of linear motors 10 and 20 that are slidably disposed on the inner peripheral surface. The stators 11 and 21 include outer yokes 11a and 21a made of a magnetic material and coils 11b and 21b. The movable bodies 12 and 22 include inner yokes 12a and 22a of magnetic material, permanent magnets 12b and 22b, compression pistons 12c and 22c, and adjustment members 12d and 22d. A first compression space 6 (compression space) is formed between the compression pistons 12c and 22c, and buffer spaces 13 and 23 are formed on the opposite sides of the compression pistons 12c and 22c to the first compression space 6, respectively. The buffer spaces 13 and 23 have the same volume, and the linear motors 10 and 20 are the same.

  In the cooling unit 30, the flow path 4b communicating with the compression space 6 of the compression section 2 via the pipe 4 and the flow path 4d communicating with the second compression space 31 (compression space) are merged in the flow path 4c. The flow path 4c, the radiator 32, the regenerator 33, the heat absorber 34, the flow path 34a, and the expansion space 35 communicate with each other to form a working space and cause a vibration force of the displacer 37 that forms the expansion space 35. A vibration source 40 is provided.

  The expansion space 35 is formed by a cylinder 36, a front surface 37 a of a displacer 37 that slides on the inner peripheral surface of the cylinder 36, and a pressure vessel 38 that forms the regenerator 33.

  The second compression space 31 is formed by a normal temperature portion 36 a of the cylinder 36, a rear surface 37 b of the displacer 37, and a rod 42 of the vibration source 40 connected to the center of the rear surface 37 b of the displacer 37. A large number of channel holes 4d provided on the side and the ring-shaped channel 4c communicate with the radiator 32.

  The regenerator 33 is formed by stacking regenerator elements 33 a such as a wire mesh, and heat exchange is performed between the regenerator element 33 a and helium flowing through the regenerator 33. The radiator 32 exhausts heat of compression of helium to the outside. The heat absorber 34 is cooled by being brought into thermal contact with the cooled object 50 through the wall of the pressure vessel 38. In addition, when not installing the heat absorber 34, the low temperature part 38a of the pressure vessel 38 becomes a heat absorber.

  FIG. 2 is an enlarged view of the vibration source 40 of FIG. The vibration source 40 includes a case 41 that is disposed in a normal temperature portion 36a (fixing member) of the cylinder 36 and that houses a support member 43 in which a rod 42 whose axis is located on the central axis A is disposed. The axis 41d is located on the central axis A.

  The support member 43 includes a disc-shaped flange portion 43c and columnar portions 43a and 43b at the center of both surfaces of the flange portion 43c. The axes of the columnar portions 43a and 43b of the support member 43 are the center axis A of the displacer 37. Located on the top. The support member 43 is provided with first bearings 44 and 45 (first sliding member) made of a resin sliding material on both surfaces of the flange portion 43c.

  The first bearings 44 and 45 are L-shaped in cross section and the axis is located on the central axis A, and are composed of disk parts 44a and 45a and cylindrical parts 44b and 45b on the inner peripheral side of the disk parts 44a and 45a, The inner peripheral surfaces 44c and 45c (rotation guides) of the cylindrical portions 44b and 45b fit with the outer peripheral surfaces of the columnar portions 43a and 43b of the support member 43 with a slight gap, and rotate smoothly around the central axis A. it can.

  On the inner surfaces 41a and 41b of the case 41, second bearings 46 and 47 (second sliding members) made of a resin sliding material are provided. The second bearings 46 and 47 have an L-shaped cross section and the shaft is located on the central axis A, and are composed of disk portions 46a and 47a and cylindrical portions 46b and 47b on the inner peripheral side of the disk portions 46a and 47a. The outer peripheral surfaces 46c and 47c (rotation guides) of the disk portions 46a and 47a are engaged with the inner peripheral surface 41d of the case 41 with a slight gap, and can rotate smoothly around the central axis A.

  A coil spring 48 is provided between the first bearing 44 and the second bearing 46, and the inner diameters of both ends of the coil spring 48 are the outer peripheral surface of the cylindrical portion 44 b (guide portion) of the first bearing 44 and the cylindrical portion of the second bearing 46. 46b (guide part) is mounted on the outer peripheral surface with a slight gap. Similarly, a coil spring 49 is provided between the first bearing 45 and the second bearing 47, and the inner diameters at both ends of the coil spring 49 are the outer peripheral surface of the cylindrical portion 45 b (guide portion) of the first bearing 45 and the second bearing 47. The cylindrical portion 47b (guide portion) is attached to the outer peripheral surface with a slight gap. In this way, the pair of coil springs 48 and 49 are disposed opposite to each other with the support member 43 interposed therebetween, and the cylindrical portions 44b, 45b, 46b, 47b direct the spring force due to contraction and relaxation of the coil springs 48, 49 toward the central axis A. Become a guide.

  A ring 41c made of a resin sliding material is inserted and fixed in a hole provided in the center of the inner surface 41a of the case 41, and the rod 42 penetrates the inner peripheral surface of the ring 41c with a small gap, and the end of the rod 42 is inserted. Is connected to the center of the back surface 37b of the displacer 37. The ring 41c functions as a clearance seal that seals the bearing and helium.

  In the above description, the material of the first bearings 44 and 45 is a resin sliding material, but the support 43 may be a resin sliding material and the first bearings 44 and 45 may be metal.

  Next, the operation and effect of the present invention will be described.

  As will be described later, the displacer 37 and the movable bodies 12 and 22 form a vibration system having a specific resonance frequency of the spring and the mass, respectively, and the mass of the adjustment masses 12 and 22 is increased or decreased. By adjusting the resonance frequency of 22 to the resonance frequency of the displacer 37, the volume of the expansion space 35 is advanced by about 90 degrees with respect to the total volume of the first compression space 6 and the second compression space 31, and with less power. A large amount of refrigeration is obtained and cooling can be performed efficiently.

  When the linear motors 10 and 20 are energized with the combined resonance frequency current, the movable bodies 12 and 22 reciprocate, and the displacer 37 reciprocates accordingly. The coil springs 48 and 49 contract the coil springs 48 and 49. The relaxation causes spring force and torsional force. Here, the spring force is a compressive force in the axial direction of the coil springs 48 and 49, and the torsional force is a force in the winding direction of the spring (force in the circumferential direction). The axial compressive force, that is, the spring force, causes the reciprocating motion of the displacer 37 described above, and the torsional force of the coil springs 48 and 49 swings the first bearings 44 and 45 and the second bearings 46 and 47, respectively. Acts as a rotational force for sliding.

  Since the inner peripheral surfaces of the cylindrical portions 44b and 45b of the first bearings 44 and 45 are engaged with the cylindrical portions 43a and 43b of the support device 43 with a slight gap, the rotation shafts of the first bearings 44 and 45 are Fits the central axis A. Further, since the outer peripheral surfaces of the disk portions 46a and 47a of the second bearings 46 and 47 are engaged with the inner peripheral surface 41d of the case 41 with a slight gap, the centers of the second bearings 46 and 47 are center axes. Fits A.

  When the aforementioned rotational force is applied, the frictional force between one end surface of the coil spring 48 and the first bearing 44 is larger than the frictional force between the first bearing 44 and the flange portion 44c of the support member 43. One end surface of 48 does not slide on the surface of the first bearing 44, and the first bearing 44 swings and slides smoothly around the central axis A of the displacer 37 on the surface of the flange portion 44 c of the support member 43. Similarly, since the frictional force between the other end surface of the coil spring 48 and the second bearing 46 is larger than the frictional force between the second bearing 46 and the inner surface 41a of the case 41, the other end surface of the coil spring 48 is the second bearing 46. The second bearing 46 smoothly swings and slides around the central axis A on the inner surface 41a of the case 41 without sliding on the surface. Further, the first bearing 45 and the second bearing 47 operate in the same manner as described above. Accordingly, each of the bearings 44, 45, 46 and 47 smoothly swings and slides, so that the first bearing 44, the second bearing 46 and the coil spring 48, and the first bearing 45, the second bearing 47 and the coil spring 49 are There is no generation of abrasion powder due to biting of the coil spring end face into the sliding surface of the prior art, and it is possible to provide a regenerative refrigerator 1 having a high cooling efficiency and a stable refrigeration capacity that can be stably operated for a long period of time.

  The inner diameter of one end of the coil springs 48 and 49 is mounted with a slight gap with respect to the outer peripheral surface of the cylindrical portions 44b and 45b of the first bearings 44 and 45, and the inner diameter of the other end is second. The bearings 46 and 47 are mounted with a slight gap on the outer peripheral surfaces of the cylindrical portions 46b and 47b. That is, each cylindrical portion 44b, 45b, 46b, 47b acts as a guide portion that directs the spring force caused by the contraction and relaxation of the coil springs 48, 49 toward the central axis A. Accordingly, since the direction of the spring force due to the contraction and relaxation of the coil springs 48 and 49 is on the central axis A, the moment due to the contraction and relaxation spring force does not act on the rod 42 or the displacer 37, and the rod 42 or the displacer. 37 reciprocates smoothly, and does not reciprocate with the conventional technique, reducing mechanical loss and increasing the amplitude of the displacer 37. As a result, the refrigeration capacity is stabilized and the cooling efficiency is increased.

  Since the cylindrical portions 44b and 45b and the cylindrical portions 46b and 47b are both arranged on the inner circumferences of the first bearings 44 and 45 and the second bearings 46 and 47, the inner diameters of the coil springs 48 and 49 are set to the cylindrical portions 44b and 45b. By mounting with a slight gap on the outer peripheral surfaces of the cylindrical portions 46b and 47b, when the coil springs 48 and 49 are contracted, the gaps are expanded, and the inner diameter dimensions of the coil springs 48 and 49 can be expanded without restriction. As a result, the displacer 37 or the rod 42 reciprocates smoothly, the mechanical loss is reduced, and the amplitude of the displacer 37 is increased. As a result, the refrigeration capacity is stabilized and the cooling efficiency is increased.

  Further, since 44b, 45b, 46b, and 47b are cylinders, the shape is simple and the cost is low.

  Next, the spring / mass vibration system of the displacer 37 and the movable bodies 12 and 22 will be described. A vibration having a specific resonance frequency of the spring and the mass of the magnetic spring of the linear motors 10 and 20, the combined spring of the gas spring of the compression space 6, the gas spring of the buffer spaces 13 and 23, and the mass of the movable bodies 12 and 22. When a system is formed and a current of this resonance frequency is applied to the linear motors 10 and 20, the strokes of the reciprocating motions of the movable bodies 12 and 22 increase, and helium is efficiently compressed in the compression space 6.

  When the movable bodies 12 and 22 reciprocate, helium causes pressure fluctuations at the same frequency, and the displacer 37 reciprocates at the same frequency. That is, the displacer 37 has a force due to pressure acting on the front surface 37 a and the back surface 37 b of the displacer 37, a force due to pressure acting on the lower end surface of the rod 42 (pressure in the case 41), and coil springs 48 and 49. The resultant force of the spring force generated by contraction and relaxation balances with the inertial force of the total mass described below and reciprocates. In this case, since the pressures of the front surface 37a and the rear surface 37b of the displacer 37 are substantially equal and the rod diameter is small, the spring constant of the gas spring is sufficiently smaller than the spring constant of the coil spring. The vibration of the reciprocating motion of the support 37 is caused.

  The displacer 37 is composed of coil springs 48 and 49, a gas spring in the expansion space 35, a gas spring in the second compression space 31, and a gas spring in the case 41, a mass of the displacer 37, a mass of the rod 42, and a holding force. The total mass of the mass of the device 43 and the mass of the first bearings 44 and 45 forms a vibration system having an inherent resonance frequency of the spring and mass, and the displacer 37 reciprocates at this resonance frequency. The stroke increases and a large amount of refrigeration is generated in the expansion space 35.

  The regenerative refrigerator 1 generates refrigeration as follows. The helium in the first compression space 6 and the second compression space 31 compressed in the compression stroke by the movable bodies 12 and 22 and the displacer back surface 37b is cooled by the radiator 32 and the regenerator 33, and the expansion stroke of the displacer front surface 37a. And the refrigeration is generated in the expansion space 35. Next, the helium flowing out from the expansion space 35 in the discharge stroke (compression stroke) of the displacer front surface 37a is warmed by the regenerator 33 and returned to the first compression space 6 and the second compression space 31, and one cycle of the Stirling refrigerator is performed. finish.

(Example 2)
FIG. 3 is a sectional view of another cold storage type refrigerator according to the present invention. In addition, since the structure of the compression part of FIG. 3, piping, a flow path, a heat radiator, a cool storage, a heat absorber, and a pressure vessel is the same as FIG. 1, it attaches | subjects the code | symbol of FIG. The regenerative refrigerator 60 is configured by connecting the compression section 2 and the cooling section 70 via the pipe 4 to the flow path holes 4a and 4b provided in the respective sections, and filled with helium (working gas). A pulse tube refrigerator 60 (cool storage type refrigerator) using a displacer 77 described later as a phase adjuster is formed.

  In the cooling unit 70, the flow path 4b communicating with the first compression space 6 (compression space) and the flow path 4d communicating with the second compression space 71 (compression space) merge at the flow path 4c. 4 c, radiator 32, regenerator 33, heat absorber 34, flow path 34 a, expansion circuit 75 formed in communication, and gas formed adjacent to displacer 77 that forms expansion space 75. A vibration source 80 that includes the piston 78 and causes the reciprocation of the displacer 77 is provided.

  The expansion space 75 includes a cylinder 76, a dashed-dotted gas piston 78 formed on the front surface 77 a of the displacer 77 that slides on the inner peripheral surface of the cylinder 76, and a pressure vessel 38 that forms the regenerator 33. Formed from. The displacer 77 is formed by screwing a resin sliding material cap 77d into the opening of the piston portion 77c of the resin sliding material, and is short and does not extend to the low temperature side like the displacer 37 of FIG. The length is such a length that the temperature of the front surface 77a is intermediate between the low temperature and the normal temperature, and the displacer 77 functions as a phase adjuster that determines the phase of the gas piston 78.

  The second compression space 71 (compression space) passes through a hole 77e provided in the center of the room temperature portion 76a of the cylinder 76, the back surface 77b of the displacer 77, and the back surface 77b of the displacer 77, and is a rod disposed in the vibration source 80. 82, and communicates with the radiator 32 through a large number of passage holes 4d provided on the room temperature side of the cylinder 76 and the ring-like passage 4c. The first compression space 6 communicates with the radiator 32 sequentially through the flow path hole 4a, the pipe 4, the flow path hole 4b, and the flow path 4c.

  FIG. 4 is an enlarged view of the vibration source 80 of FIG. The vibration source 80 is provided in a normal temperature part of the displacer 77, and the normal temperature part of the displacer 77 becomes a case 81 of the vibration source 80. The case 81 houses a support member 83 provided with a rod 82.

  The support member 83 includes a disk-shaped flange portion 83c and cylindrical portions 83a and 83b at the center of both surfaces of the flange portion 83c. The axis of the rod 82 and the axes of the cylindrical portions 83 a and 83 b of the support member 83 are located on the central axis B of the displacer 77. The support member 83 is provided with first bearings 84 and 85 (first sliding member) made of a resin sliding material on both surfaces of the flange 83c.

  The first bearings 84 and 85 have an axis located on the central axis B, an L-shaped cross section, and are composed of disk parts 84a and 85a and cylindrical parts 84b and 85b on the inner peripheral side of the disk parts 84a and 85a. The inner peripheral surfaces 84c and 85c (rotational guide) of the cylindrical portions 84b and 85b are fitted with the outer peripheral surfaces of the columnar portions 83a and 83b of the support member 83 with a slight gap, and smoothly around the central axis B. Can rotate.

  In the case 81, the axis of the inner peripheral surface 81d is located on the central axis B, and second bearings 86 and 87 (second sliding members) are provided on the inner surfaces 81a and 81b at both inner ends. The second bearings 86 and 87 have an axis located on the central axis B, an L-shaped cross section, and are composed of disk parts 86a and 87a and cylindrical parts 86b and 87b on the inner peripheral side of the disk parts 86a and 87a. The outer peripheral surfaces 86c and 87c (rotation guide) of the disk portions 86a and 87a are fitted with the inner peripheral surface 81d of the case 81 with a slight gap, and the second bearings 86 and 87 are smoothly around the central axis B. Can be rotated.

  A coil spring 88 is provided between the first bearing 84 and the second bearing 86, and the inner diameters at both ends of the coil spring 88 are respectively the outer peripheral surface of the cylindrical portion 84 b (guide portion) of the first bearing 84 and the second bearing 86. The cylindrical portion 86b (guide portion) is attached to the outer peripheral surface with a slight gap. Similarly, a coil spring 89 is provided between the first bearing 85 and the second bearing 87. The inner diameters of both ends of the coil spring 89 are mounted with a slight gap on the outer peripheral surface of the cylindrical portion 85b (guide portion) of the first bearing 85 and the outer peripheral surface of the cylindrical portion 87b (guide portion) of the second bearing 87, respectively. . In this way, the pair of coil springs 88 and 89 are arranged to face each other with the support member 83 interposed therebetween, and the cylindrical portions 84b, 85b, 86b and 87b apply the spring force of the coil springs 88 and 89 to the central axis B of the displacer 77. It becomes the guide part to turn.

  The rod 82 protrudes from the case 81 with a minute gap with respect to a hole 77e provided at the center of the back surface 77b of the displacer 77, and the normal temperature of the cylinder 76 is set so that the axis of the rod 82 is positioned on the central axis B of the displacer 77. It is connected to the inner surface center of the part 76a (connecting member). The hole 77e functions as a clearance seal that seals the bearing and helium.

  Next, the operation and effect of the present invention will be described.

  One of the differences between the vibration source 80 and the vibration source 40 of FIG. 1 is that the vibration source 80 is provided in the displacer 77. That is, in the case of FIG. 1, since the case 41 is fixed to the normal temperature portion 36 of the cylinder 36, the support member 43, the rod 42, and the displacer 37 reciprocate together, whereas FIG. In this case, since the rod 82 is connected to the center of the inner surface of the normal temperature portion 76a of the cylinder 76, the spring force caused by the contraction and relaxation of the coil springs 88 and 89 is affected by the case 81, that is, the displacer 77 via the second bearings 86 and 87. And the displacer 77 reciprocates.

  The action of the vibration source 80 is the same as the action of the vibration source 40 of FIG. 1, and for the same reason, it is possible to provide a regenerative refrigerator 60 that can operate stably for a long period of time, has a stable refrigeration capacity, and has a high cooling efficiency. .

Further, since the vibration source 80 is provided in the displacer 77, the length of the cooling unit 70 is shortened, and the cooling unit 70 is reduced in size.

  Another difference is that the expansion space 75 is formed by the gas piston 78. That is, the expansion space 35 in FIG. 1 is formed by a displacer 37 that is a solid piston, and the volume of the displacer 37 is always constant regardless of the pressure fluctuation of helium. In the case of FIG. Since it is formed by the gas piston 78, the mass of the gas piston 78 does not change at a constant value, but the volume increases or decreases with the pressure fluctuation of helium.

  The effect of freezing is the same as in FIG. 1 except that the volume of the gas piston 78 increases or decreases with the pressure fluctuation of helium. Further, since the displacer 77 does not extend to the low temperature side, the helium sealing pressure must be increased in order to obtain the same pressure amplitude as in FIG. 1, but the displacer 77 is in contact with the low temperature side of the cylinder 76. In addition, the heat loss of frictional heat due to the contact of the displacer in the expansion space 75 does not occur. As a result, it is possible to provide a regenerative refrigerator 60 having a stable refrigeration capacity and high cooling efficiency.

  Note that the length of the displacer 77 may be further shortened so that the front surface 77a of the displacer 77 has a substantially normal temperature. In this case, the displacer 77 becomes the case 81 of the vibration source 80. 1 may be formed by shortening the length of the displacer 37. In this case, the gas piston is formed on the front surface 37a of the displacer 37. It becomes a machine.

Example 3
FIG. 5 is an enlarged view of the cross section of the vibration source of the regenerative refrigerator according to the present invention, which is another embodiment of the vibration source 40 shown in FIG. In FIG. 5, members having the same shape as the vibration source 40 of FIG. The vibration source 90 in FIG. 5 differs from the vibration source 40 in FIG. 1 in that the first (first sliding member) 94 and 95 and the second bearings 96 and 97 (second sliding member) in FIG. This is different from the first bearings 44 and 45 and the second bearings 46 and 47 in FIG. 1. In other words, the first bearings 94 and 95 of the resin sliding material have an axis positioned on the central axis A of the displacer 37 and a L-shaped cross section, and the disk portions 94a and 95a and the disk portions 94a and 95a, respectively. Cylindrical portions 94b and 95b are provided on the outer peripheral side. The inner peripheral surfaces 94c and 95c (rotation guides) of the disk portions 94a and 95a are fitted with a slight gap with respect to the outer peripheral surfaces of the cylindrical portions 43a and 43b of the support member 43, and around the center axis A of the displacer 37. Can smoothly slide and rotate. Similarly, the second bearings 96 and 97 of the resin sliding material have an axis positioned on the central axis A of the displacer 37 and an L-shaped cross section, and the disk portions 96a and 97a and the disk portions 96a and 97a. Cylindrical portions 96b and 97b are provided on the outer peripheral side. The outer peripheral surfaces 96c and 97c (rotation guide) of the cylindrical portions 96b and 97b are mounted with a slight gap with respect to the inner peripheral surface 41d of the case 41, and can smoothly slide and rotate around the central axis A of the displacer 37.

  A coil spring 48 is provided between the disc portion 94a of the first bearing 94 and the disc portion 96a of the second bearing 96, and the outer diameters of both ends of the coil spring 48 are respectively the cylindrical portions 94b (guide portions) of the first bearing 94. The inner circumferential surface and the inner circumferential surface of the cylindrical portion 96b (guide portion) of the second bearing 96 are mounted with a minute gap. Similarly, a coil spring 49 is provided between the disc portion 95a of the first bearing 95 and the disc portion 97a of the second bearing 97, and the outer diameters of both ends of the coil spring 49 are respectively cylindrical portions 95b (guides) of the first bearing 95. Part) and the inner peripheral surface of the cylindrical part 97b (guide part) of the second bearing 97 with a small gap. In this case, the cylindrical portions 94b, 95b, 96b, and 97b serve as guide portions that direct the spring force generated by the contraction and relaxation of the coil springs 48 and 49 toward the central axis A.

  The cylindrical portions 94b and 95b of the first bearings 94 and 95 and the cylindrical portions 96b and 97b of the second bearings 96 and 97 are provided on the outer peripheral side of the disc portions 94a and 95a and on the outer peripheral side of the disc portions 96a and 97a, respectively. When the coil springs 48 and 49 are contracted, the gaps between the coil springs 48 and 49 and the cylindrical portions 94b, 95b, 96b, and 97b are contracted. Therefore, a slight gap must be secured in the maximum contracted state of the coil springs 48 and 49. . Other actions and effects of the vibration source 90 are the same as the actions and effects of the vibration source 40 of FIG.

It is sectional drawing of the cool storage type refrigerator of 1st Example concerning this invention. It is an expanded sectional view of the vibration source of FIG. It is sectional drawing of the cool storage type refrigerator of 2nd Example concerning this invention. FIG. 4 is an enlarged view of the vibration source of FIG. 3. It is an expanded sectional view of 3rd Example concerning this invention.

Explanation of symbols

1, 60 Regenerative refrigerator 6 First compression space (compression space)
31, 71 Second compression space (compression space)
32 radiator 33 regenerator 35, 75 expansion space 36a normal temperature part (fixing member)
37, 77 Displacer 37b Rear surface 40, 80, 90 Vibration source 41, 81 Case 43, 83 Support member 42, 82 Rod 48, 49, 88, 89 Coil spring 44, 45, 84, 85, 94, 95 First bearing ( First sliding member)
44c, 45c, 84c, 85c, 94c, 95c Inner peripheral surface (rotation guide)
46, 47, 86, 87, 96, 97 Second bearing (second sliding member)
46c, 47c, 86c, 87c, 96c, 97c Outer peripheral surface (rotation guide)
44b, 45b, 46b, 47b, 84b, 85b, 86b, 87b, 94b, 95b, 96b, 97b Cylindrical part (guide part)
76a Normal temperature part of cylinder (connecting member)
A, B Center axis

Claims (6)

A compression space for compressing the working gas;
A radiator that dissipates heat of the working gas compressed in the compression space;
A regenerator that exchanges heat with the working gas that reciprocates through the radiator;
An expansion space provided with a displacer for expanding the working gas cooled by the regenerator;
A regenerative refrigerator having a vibration source that causes reciprocation of the displacer,
The vibration source includes a case through which a rod positioned on the central axis of the displacer passes, a support member accommodated in the case and provided with the rod, and a rotatable guide provided on both sides of the support member and rotatable. A first sliding member provided; a second sliding member provided with a rotatable guide disposed on both inner surfaces of the case; and between the first sliding member and the second sliding member. A regenerative refrigerator having a deployed coil spring and a guide portion that is attached to the coil spring and that directs the direction of the spring force of the coil spring acting on the displacer in the direction of the central axis. 2. The regenerative refrigerator according to claim 1, wherein the vibration source is disposed on a fixing member located on a facing side of the back surface of the displacer and connects the rod to the back surface of the displacer. 2. The regenerative refrigerator according to claim 1, wherein the vibration source is disposed in the displacer, and the rod is connected to a connecting member facing the side through which the rod passes from the vibration source. The regenerative refrigerator according to any one of claims 1 to 3, wherein the guide portion is arranged on at least one of the first sliding member and the second sliding member. The regenerative refrigerator according to any one of claims 1 to 4, wherein the guide portion is disposed on an inner periphery of the first sliding member and the second sliding member. The regenerative refrigerator according to any one of claims 1 to 5, wherein the guide portion is a cylinder.

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