JPH0424619B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an oil-fed Stirling cycle refrigerator equipped with a radial piston compressor.

(Prior Art) It is well known that in a Stirling cycle refrigerator, it is necessary to cause a compression piston and a displacer to reciprocate under a constant phase difference. Known drive systems for the compression piston and displacer to generate such motion include a crankshaft drive system, a rotating swash plate drive system, a Rhombic drive system, and a linear drive system. The drive system and linear drive system are drive systems for single-cylinder engines, and are not suitable for multi-cylinder systems.

Therefore, conventional techniques are known in which the crankshaft drive system (see Japanese Patent Application Laid-open No. 58-69366) or the rotary swash plate drive system (see Japanese Patent Application Laid-Open No. 54-149958) is used for multi-cylinder applications.

The above crankshaft drive system is constructed by arranging multiple cylinders coaxially in series and connecting the compression piston inserted in one cylinder and the displacer inserted in the other cylinder in the axial direction. The above rotating swash plate drive system has a plurality of cylinders arranged concentrically, and a compression piston inserted into one cylinder and a displacer inserted into the other cylinder are arranged parallel to each other. It is composed of Both of these types can be made to have multiple cylinders relatively easily.

(Problems to be Solved by the Invention) However, the above-mentioned prior art has a drawback that the structure is complicated, and in order to obtain a large output, the overall weight and size must be increased. In particular, the rotating swash plate drive system is generally suitable for small refrigerators.
It is necessary to increase the diameter of the swash plate according to the piston diameter, and the strength of the swash plate and bearing part must be increased accordingly, so if you aim for high output, the equipment will become larger as necessary. .

This invention was made to solve the above-mentioned conventional problems, and its purpose is to provide a multi-cylinder oil-fed Stirling cycle refrigerator that has a simple structure, is compact, lightweight, and has high reliability. do.

(Means for Solving the Problems) In order to achieve the above object, the present invention radially arranges a plurality of compression pistons and a crosshead coaxially connected to each compression piston via a piston rod. A radial type piston drive device is constructed by slidingly contacting the connecting rod of the crosshead with the eccentric body of the crankshaft which is rotationally driven by the drive machine. In addition, a plurality of displacers are installed concentrically with the crankshaft, and a cam groove that is displaceable in the axial direction of the crankshaft is provided on the outer periphery of a cam member fixed to one end of the crankshaft. A displacer drive device is constructed by inserting a drive body and connecting a rod for reciprocating the displacer in the axial direction of the crankshaft to the drive body. The shape of the cam groove is set so that the phase of the displacer corresponding to each compression piston can advance approximately 90 degrees. Further, lubricating oil is supplied to the crosshead chamber between the compression piston and the crosshead by a lubricating oil supply device, and a passage for passing this lubricating oil is provided.
It extends into the connecting rod from the crosshead side.
One end of this passage opens into the crosshead chamber, and the other end opens into a sliding contact between the connecting rod and the body. Furthermore, a shielding member is fixed to the cylinder into which the compression piston and crosshead are inserted, which shields between the rear chamber of the compression piston and the crosshead chamber, and this shielding member has the following features:
The piston rod is slidably inserted therethrough. Furthermore, the gap between the shielding member and the piston rod is hermetically sealed by a sealing device.

(Function) According to the present invention, a radial piston drive device and a displacer drive device having a plurality of displacers arranged concentrically with the crankshaft of the piston drive device are combined to produce a Stirling cycle refrigeration system. With this structure, even if the number of compression pistons and displacers is increased to improve the refrigerating capacity, the overall size of the refrigerating machine can be avoided.

Furthermore, since a radial piston drive mechanism is employed, most of the gas compression loads are canceled out in the compression chamber, making it possible to maintain the balance of compression forces relatively easily. Therefore, the load on the bearing section that supports the crankshaft can be reduced, so that the casing and the bearing section can be made more compact as a whole.

Furthermore, since the compression piston and the crosshead are arranged radially, even if the diameter of the piston is increased, the overall size of the device does not increase. Therefore, the output can be easily increased.

In addition, the lubricating oil supplied to the crosshead chamber is
Since the crosshead bearings are supplied through passages extending from within the crosshead into the connecting rods, frictional heat generation in the bearings is prevented. This prevents parts from being worn out, improves reliability, and extends the life of the bearing. Furthermore, a shielding member that shields the crosshead chamber and compression is fixed to the cylinder, the piston rod is slidably passed through the shielding member, and the gap between the piston rod and the shielding member is airtightly sealed. lubricating oil is prevented from entering the compression chamber. Thereby, the inside of the compression chamber can be kept clean at all times, and the refrigerant can be prevented from being contaminated by oil.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view of a refueled Stirling cycle refrigerator. In the figure, a refueled Stirling cycle refrigerator 1 includes a radial piston drive device 2 and a displacer drive device 3 connected to each other.

The piston drive device 2 includes a speed reducer 5 and a drive device 6, and the speed reducer 5 is, for example, a planetary gear mechanism or a bevel gear mechanism. One end of the drive shaft (not shown) of the reducer 5 is connected to a crankshaft 4 that extends in a direction perpendicular to the direction in which the drive device 6 and the reducer 5 are connected (left-right direction in FIG. 1). ,
The other end of the drive shaft on the side opposite to the crankshaft 4 is connected to a lubricating oil pump 70 with a pressure regulating valve. The lubricating oil pump 70 is driven by the speed reducer 5 and plays a role of supplying lubricating oil under pressure to an oil supply pipe 71 which will be described later. The crankshaft 4 passes vertically through the airtight crankcase 7, and is rotatably supported within the crankcase 7 by roller bearings 8a, 8b. The body 9 of the crankshaft 4 is
It has a larger diameter than the crankshaft 4 and is eccentric to the crankshaft 4. The diameter and eccentric width of the trunk 9 are:
The compression piston 17 is selected depending on the stroke.

As shown in FIG. 2, the crankcase 7 has four crosshead cylinders 11 and four compression piston cylinders 18 coaxially connected to each cylinder 11, which are arranged radially in the radial direction of the crankshaft 4. It is installed protrudingly. A shielding member 50 is fixed between the cylinders 11 and 18, respectively.
The rear chamber 2 inside the cylinder 18 is protected by the shielding member 50.
1 and the crosshead chamber 16 within the cylinder 11 are shielded. The shielding member 50 consists of a cylindrical portion 51 and a flange portion 52. The cylindrical portion 51 extends coaxially with the cylinders 11 and 18, and has a piston rod 15 extending from the compression piston 17 in its shaft hole.
penetrates freely. An annular seal chamber 56 surrounding the piston rod 15 is formed within the cylindrical portion 51 . Further, the lower end portion 53 of the cylindrical portion 51 is fitted into the cylinder 11, and the flange portion 52 is
It is flange-coupled to the bottom portion 18a of the cylinder 18 and the flange portion 11a of the cylinder 11. Note that 57 and 58 are seal rings, 59 is an oil stopper ring, and 57a and 58a are seal ring holders.

As shown in FIG. 1, the crosshead 12 is connected to one end 15a of the piston rod 15, and is connected to the spherical head 13C of the connecting rod 13 via a spherical bearing 19. A plurality of inclined passages 60 are formed within the crosshead 12 and branch radially around the spherical bearing 19.
The outer end of the inclined passage 60 opens toward the crosshead chamber 16 from the peripheral edge of the head surface 61.
An inner end of the inclined passage 60 communicates with one end of a straight passage 62 extending from inside the spherical head 13C into the connecting rod 13, and the other end of the straight passage 62 communicates with the body 9.
Slide bearing 13 of connecting rod 13 in sliding contact with the outer peripheral surface of
It opens at a. Note that 62a is a straight passage 62
It is a diaphragm installed inside.

A guide ring 14 is in contact with each flange portion 13b of the connecting rod 13, so that the sliding movement of the connecting rod 13 is performed smoothly. Also, the piston ring 2 of the compression piston 17
2 and the rider ring 23 are both made of non-lubricated material.

In the compression chamber 20 and the back chamber 21, a working gas as a refrigerant, for example He gas at a constant pressure, is contained.
Each of the crosshead chambers 16 is filled with lubricating oil supplied from a lubricating oil pump 70. The compression chamber 20 communicates with the back chamber 21 via a first bypass pipe 64, and a check valve 65 is provided in the middle of the first bypass pipe 64. Check valve 65
allows the gas to flow from the back chamber 21 to the compression chamber 20, thereby reducing the drop in the maximum pressure of the compression chamber 20 caused by the gas in the compression chamber 20 passing through the piston ring 22 and flowing into the back chamber 21. It plays a role in preventing. On the other hand, the back chamber 21 communicates with the seal chamber 56 via a second bypass pipe 66 and a passage 67. In the middle of the second bypass pipe 66,
A check valve 68 is provided, and an oil adsorption portion 69 is interposed between the check valve 68 and the passage 67. The check valve 68 serves to compensate for gas leakage from the back chamber 21 to the seal chamber 56 via the seal ring 58. In addition, the back chamber 21
As shown in FIG. 2, the third bypass pipe 7
2 to each back chamber 2 of the other three cylinders 11
1, thereby canceling out gas pressure changes due to changes in volume of each back chamber 21 during operation, and keeping each back chamber 21 at an equal pressure.

As shown in FIG. 3, a ring-shaped oil supply pipe 71 extending between the cylinders 11 is attached to the outside of the crosshead cylinders 11. As shown in FIG. The inlet hole 73 of the oil supply pipe 71 communicates with the lubricating oil pump 70 (FIG. 1) via a pipe (not shown), and each outlet 74 provided corresponding to the cylinder 11 communicates with the lubricating oil pump 70 (FIG. 1) through a pipe (not shown). As shown in Cylinder 1
It communicates with one end of each communication hole 75 drilled in 1. The other ends of the communication holes 75 are open facing the crosshead chamber 16, respectively.

The crank case 7 also includes a crank chamber 80.
An oil drain hole 76 is provided for discharging the lubricating oil guided inside to the lubricating oil pump 70 side.

Next, the configuration of the displacer drive device 3 will be explained. A cam member 30 coaxial with the crankshaft 4 is provided at the upper end of the crankshaft 4 in FIG. A key 31 is fitted between the crankshaft 4 and the cam member 30 for transmitting rotational motion. A cam groove 32 having a rectangular cross section and extending in the circumferential direction is formed on the outer peripheral surface of the cam member 30. The cam groove 32 is curved in a sinusoidal shape in the circumferential direction, and four roller-shaped drive bodies 33 are installed in the cam groove 32 at equal intervals in the circumferential direction.
is inserted. Each drive body 33 is connected to the crankshaft 4 by a crease-sealed roller bearing (not shown).
The four rods 34 are individually fastened by bolts and nuts 95 to four rods 34 arranged concentrically with the crankshaft 4 so as to be rotatable about an axis perpendicular to the crankshaft 4 . Each rod 34 extends coaxially with the crankshaft 4 and is reciprocatably supported within the airtight casing 28 by low vapor pressure, grease-sealed bearings 36a, 36b.

Each rod 34 is individually connected to each displacer 41 in four displacer cylinders 40 extending coaxially with the rod 34.
The displacer 41 has a relatively large diameter first displacer 41 connected to the tip of the rod 34.
a, and a relatively small-diameter second displacer 41b connected to the first displacer. 1st
An airtight back chamber 42 is provided at the connection between the displacer 41a and the rod 34, and the back chamber 42 is connected to the compression chamber 20 in the compression piston cylinder 18 via a passage 43 and a heat exchanger 44. is connected to. The heat exchanger 44 is configured by incorporating a plurality of water cooling pipes.

Inside the first displacer 41a, a first regenerator 38a made up of layered wire mesh (cold storage material) is incorporated, and inside the second displacer 41b, lead particles (cold storage material) are incorporated. A second regenerator 38b filled with water is incorporated. 1st displacer 4
1a and the second displacer 41b is provided with an airtight first expansion chamber 46a, and in the vicinity of this first expansion chamber 46a, each first expansion chamber of the displacer cylinder 40 is provided. A first annular cold head 47a is provided which communicates with all of the cold heads 46a. Further, an airtight second expansion chamber 46b is provided at the tip of the second displacer 41b, and each second expansion chamber of the displacer cylinder 40 is provided in the vicinity of the second expansion chamber 46b. An annular second cold head 47 that communicates with all of 46b.
b is provided. First and second expansion chambers 46
a, 46b are the first and second regenerators 38a, 3
It communicates with the rear chamber 42 on the rod 34 side via 8b.

Next, the operations of the radial piston drive device 2 and the displacer drive device 3 will be explained.

First, when the drive device 6 is activated, the crankshaft 4 is reduced to a constant rotational speed by the reduction gear 5 and driven to rotate. The rotational movement of the eccentric body 9 of the crankshaft 4 is converted into a reciprocating movement of the connecting rod 13 via the sliding bearing 13a. Due to the eccentricity of the body 9, the four crossheads 12 and compression pistons 17 are approximately 90
They reciprocate within the cylinders 11 and 18, respectively, with a phase difference of degrees.

Further, the rotational torque of the crankshaft 4 is transmitted to the cam member 30, and is converted into reciprocating motion of the rod 34 via a drive body 33 inserted into the cam groove 32 of the cam member 30. Due to the sinusoidal shape of the cam groove 32, the four displacers 41 move toward the cylinder 40 90 degrees ahead of the phase of the corresponding compression piston 17.
Each moves back and forth inside.

On the other hand, the lubricating oil pump 70 directly connected to the reducer 5 is driven by the operation of the driving machine 6, and thereby,
Lubricating oil is supplied into the oil supply pipe 71 at a predetermined pressure, and is further supplied into the crosshead chamber 16 from each outlet hole 74 through a communication hole 75. The lubricating oil in the crosshead chamber 16 flows as the crosshead 12 reciprocates and lubricates the inner peripheral surface of the cylinder 11. A portion of the lubricating oil passes through the inclined passage 60 of the crosshead 12 to lubricate the spherical bearing 19, and further passes through the throttle 62a of the direct passage 62 to the connecting rod 13.
lubricate the sliding bearing 13a. This lubricant is
After the oil accumulates in the crank chamber 80, it is guided into the reducer 5 through the drain hole 76, and then filtered through a filter (not shown).
The oil is introduced into the lubricant pump 70 through the oil supply pipe 71, and is again circulated and supplied to the oil supply pipe 71.

Next, four steps per cycle of the Stirling cycle refrigerator 1, that is, an isothermal compression step, an isovolume step,
The isothermal expansion process and the isovolume process will be explained.

First, in the isothermal compression process, when the compression piston 17 rises from a state where the displacer 41 is located at the upper end of the displacer cylinder 40 and the compression piston 17 is located at the lower end of the compression piston cylinder 18, the compression chamber The working gas in 20 is compressed and flows into back chamber 42 through heat exchanger 44 and passage 43 . At this time, a part of the generated gas compression heat is absorbed by the water-cooled cylinder 18, and the remaining compression heat is absorbed by the heat exchanger 44, so ideally, the compression process is an isothermal compression process.

Next, in the isolysis process, the displacer 4
1 descends, the working gas in the back chamber 42 passes into the first regenerator 38a and flows into the first expansion chamber 46a, and some of the working gas flows into the second regenerator 38a.
8b and flows into the second expansion chamber 46b.
At this time, the working gas is supplied to the first and second regenerators 3
When passing through the regenerators 8a and 38b, the regenerator absorbs heat and is cooled, and the pressure also decreases, becoming a low-temperature gas at a predetermined pressure in the first and second expansion chambers 46a and 46b. This is an isolytic change with constant volume.

Next, in the isothermal expansion step, when the compression piston 17 descends, the first and second expansion chambers 46
It becomes cold due to the expansion of the low temperature gas in a and 46b.
At this time, the first and second cold heads 47
Heat is removed from a and 47b, and the low-temperature gas eventually undergoes isothermal expansion at a constant temperature. The amount of heat taken by the low temperature gas is the refrigeration output of the refrigerator 1.

Next, in the isolysis process, the displacer 4
1 rises, the first and second expansion chambers 46a,
The low temperature gas in 46b is transferred to the first and second regenerators 3
8a, 38b, flows into the rear chamber 42 on the rod 34 side, and further flows into the compression chamber 20 through the heat exchanger 44. At this time, the low-temperature gas cools each of the regenerator materials in the first and second regenerators 38a and 38b, becomes high in temperature, and increases in pressure. This is an isolytic change with constant volume.

By repeating the above series of operations, continuous refrigeration output can be obtained in the first and second cold heads 47a and 47b.

In the above configuration, a radial piston drive device 2 and a plurality of displacers 4 arranged concentrically with the crankshaft 4 of the piston drive device 2 are provided.
Since the Stirling cycle refrigerator 1 is constructed by combining the displacer drive device 3 with the displacer drive device 3 having the Enlargement can be avoided.

Furthermore, since the compression piston 17 and the crosshead 12 driven by the eccentric crank mechanism are arranged radially, most of the gas pressure load in the compression piston cylinder 18 is canceled out, and the crankshaft 4
The compressive load on the bearing that supports this can be reduced. Therefore, the bearing portion and the crankcase 7 can be made more compact.

Furthermore, since the gas pressure load is canceled out, the diameter of the compression piston 17 can be increased, thereby increasing the output. Moreover,
Since the compression piston cylinders 18 are provided radially, even if the cylinder diameter is increased, the axial dimension (vertical direction in FIG. 1) of the entire refrigerator does not increase. Furthermore, since the radial piston compressor has a structure that is flat with respect to the axial direction of the crankshaft 4, it is advantageous in reducing the axial dimension.

Further, since the forced lubrication method described below is adopted, good lubrication of each bearing portion 13a, 19 is achieved. That is, the gas pressure P1 in the compression chamber 20 during one cycle changes sinusoidally between the maximum pressure P3 and the minimum pressure P2, as shown in FIG. is maintained at a constant pressure. Here, if the pressure in the back chamber 21 is set equal to the above-mentioned minimum pressure P2, the gas load P4 acting on the compression piston 17 will be the differential pressure between the above-mentioned P1 and P2, and the crank angle of the displacer 41 will be 180 degrees to 270 degrees. In the range of , the value is almost zero. Therefore, the plain bearing 13 of the connecting rod 13
a rises above the outer peripheral surface of the moving part 9 in the above crank angle range, so the passages 60, 62
If pressure loss is ignored, lubricating oil is sufficiently supplied to the slide bearing 13a in the crosshead chamber 16 via the spherical bearing 19. This prevents the generation of frictional heat in each of the bearings 13a, 19, and extends the life of the bearings 13a, 19. Furthermore, by reducing the frictional force of the slide bearing 13a, the drive torque of the crankshaft 4 can also be reduced, and the drive shaft 6 can be made smaller.

Also, the crosshead chamber 1 is protected by the shielding member 50.
6 and the rear chamber 21, and both chambers 16, 21 are sealed with oil and gas by the seal rings 57, 58, so that the inside of the rear chamber 21 and the compression chamber 20 are always kept clean. This prevents contamination of the refrigerant gas with oil, prevents contamination of the inside of the heat exchanger 44 and the regenerator material, reduces heat transfer performance, and increases pressure loss, and improves refrigeration performance. It will be planned.

In addition, in this embodiment, a seal chamber 56 is provided between the 50 seal rings 57 and 58 of the shielding member, and an oil stopper ring 59 is attached to the piston rod 15, so that the piston can temporarily pass through one seal ring 57. Even if oil adhering to the surface of the rod 15 enters the seal chamber 56, this oil is dammed by the oil stopper ring 59 and the other seal ring 58, so that the oil is surely prevented from entering the rear chamber 21 side. Prevented. Furthermore, by filling the seal chamber 56 with refrigerant gas at a predetermined pressure and setting the pressure of the lubricating oil supplied to the crosshead chamber 16 slightly higher than the predetermined pressure in the seal chamber 56, The refrigerant gas inside the crosshead chamber 16 is prevented from flowing into the crosshead chamber 16, thereby preventing the lubricating oil from forming bubbles or becoming emulsified.

In addition, since the four crosshead chambers 16 arranged radially are communicated with each other through the oil supply pipes 71,
Changes in gas pressure due to changes in the volume of the crosshead chambers 16 due to the reciprocating movement of the crosshead 12 cancel each other out, and each crosshead chamber 16 can be maintained at an equal pressure. As a result, each crosshead chamber 16
The pressure of the lubricating oil supplied to each bearing portion 13 is approximately equal to the supply oil pressure set by the pump 70.
The amount of oil supplied to a and 19 is equalized.

Furthermore, by adjusting the opening degree of a throttle 62a provided in the middle of the straight passage 62 of the connecting rod 13, the amount of oil supplied to the slide bearing 13a can be set arbitrarily. Therefore, seizure due to friction between the guide ring 14 and the flange portion 13b of the connecting rod 13, which is caused by excessive oil supply to the slide bearing 13a, can be reliably prevented.

Furthermore, since the cam member 30 is used as a method of driving the disk spacer 41, the cam member 30
The shape of the cam groove 32 of
By making appropriate changes within a range that does not interfere with the reciprocating movement of the displacer 41, it is possible to easily achieve the most preferable reciprocating movement of the displacer 41 from a thermodynamic point of view.

Further, since the piston drive device 2 and the displacer drive device 3 are connected by the key 31 provided between the crankshaft 4 and the cam member 30,
The phase difference between the reciprocating movements of the compression piston 17 and the displacer 41 can be arbitrarily selected. This phase difference greatly affects the refrigeration output. In an ideal state, when the phase difference is 0 degrees, the refrigeration output is zero, and when the phase difference is 90 degrees, the refrigeration output is maximum. However, in reality, the optimum value exists near 90 degrees, which is slightly outside 90 degrees due to pressure loss and other factors.

In the above embodiment, the connecting rod 13 was brought into direct sliding contact with the body 9, but a bearing such as a needle bearing rig may be interposed between the connecting rod 13 and the body 9.

(Effects of the Invention) As explained above, according to the present invention, the displacer drive includes a radial piston drive device and a plurality of displacers arranged concentrically with the crankshaft of the piston drive device. Since the refrigerator is constructed by combining these devices, even if the number of compression pistons and displacers is increased in order to improve the refrigerating capacity, it is possible to avoid increasing the size of the refrigerator as a whole.

Also, the radial arrangement of the compression pistons and crossheads cancels out most of the gas pressure loads on each cylinder. Therefore, the bearing portion and the casing can be made lightweight and compact. Furthermore, even if the cylinder diameter is increased in order to increase the output, the device is prevented from becoming complicated or large.

In addition, lubricating oil is supplied into the crosshead chamber and to each bearing of the crosshead and connecting rod, which prevents wear and tear on parts due to friction.
Reliability is increased. Furthermore, the life of the bearing section is also extended. Furthermore, since the back chamber and the crosshead chamber are shielded by the shielding member, and the shielding member and the piston rod are airtightly sealed, contamination of the refrigerant with oil is reliably prevented, which improves refrigeration performance. It is possible to improve the

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view of a refueled Stirling cycle refrigerator according to the present invention, and FIG. 2 is a -
3 is a sectional view taken along the - line in FIG. 1, and FIG. 4 is a graph showing the relationship between the crankshaft and the pressure in the compression chamber. 1...Refueling type Stirling cycle refrigerator, 2
... Radial piston drive device, 3 ... Displacer drive device, 4 ... Crankshaft, 6 ... Drive machine, 9 ... Body, 12 ... Crosshead, 13
... Connecting rod, 15 ... Piston rod, 16 ... Crosshead chamber, 17 ... Compression piston, 30 ... Cam member, 32 ... Cam groove, 33 ... Drive body, 34
...Rod, 38a, 38b...Regenerator, 41...
... Displacer, 21, 42 ... Rear chamber, 44
... Heat exchanger, 46a, 46b ... Expansion chamber, 50
...shielding member, 57, 58 ... sealing device, 6
0, 62... passage, 70... lubricating oil supply device.

Claims (1)

[Claims] 1. The refrigerant compressed by the compression piston is sent through a heat exchanger to the rear chamber on one side of the displacer, passes through a regenerator in the displacer, and is expanded on the other side of the displacer. In an oil-fed Stirling cycle refrigerator that cools the refrigerant by flowing it into a chamber, a plurality of compression pistons and a crosshead coaxially connected to each compression piston via a piston rod are arranged radially. A radial piston drive device comprising a connecting rod of a crosshead in sliding contact with the eccentric body of a rotationally driven crankshaft, and a plurality of displacers arranged concentrically with the crankshaft, A cam groove that is displaceable in the axial direction of the crankshaft is provided on the outer periphery of a cam member fixed to one end, and the displacer is reciprocated in the axial direction of the crankshaft by a drive body inserted into this cam groove. a displacer drive device in which the shape of the cam member is set so that the phase of the corresponding displacer advances approximately 90 degrees with respect to each compression piston; a lubricating oil supply device for supplying lubricating oil to the crosshead chamber of the crosshead; and a lubricating oil supply device extending from the crosshead side into the connecting rod, one end opening into the crosshead chamber and the other end forming a sliding contact portion between the connecting rod and the body. a lubricating oil passageway opened to the piston rod; a shielding member fixed to the cylinder into which the compression piston and the crosshead are inserted to shield between the rear chamber of the compression piston and the crosshead chamber, and through which the piston rod is slidably passed; A refueled Stirling cycle refrigerator characterized by comprising a sealing device that airtightly seals a gap between a shielding member and a piston rod.