A valve structure capable of suppressing leakage and a refrigerator using the valve structure

Abstract

The present invention discloses a valve structure capable of suppressing leakage and a refrigerator using the valve structure. The valve structure comprises a gas distribution valve (6) provided with a high-pressure gas hole (62) and a gas distribution valve hole (63), and a rotary valve (7) provided with a low-pressure hole (71) and a high-pressure groove (72). At least one groove (11) is provided on the gas distribution valve surface (61) of the gas distribution valve (6). The groove (11) is arranged on the gas distribution valve surface (61) in an annular area defined between a first envelope S1 formed by a radial maximum circumference formed by the high-pressure groove (72) rotating relative to a rotation axis O and a second envelope S2 determined by the outer periphery of a smaller diameter component in a switching plane (73) of the rotary valve (7). At least one of the grooves (11) is located on a semicircular surface of the gas distribution valve surface (61) away from the gas distribution valve hole (63). The refrigerator is provided with the valve structure. The valve structure of the present invention can suppress gas leakage.

Description

Technical Field

[0001] This invention belongs to the field of cryogenic refrigeration technology, specifically a valve structure capable of suppressing leakage and a refrigeration machine using the valve structure. Background Art

[0002] Ultra-low temperature refrigerators, exemplified by Gifford-McMahon (GM) refrigerators, have an expander and a compressor for the working gas (also known as the refrigerant gas). Figure 1 This is the type of refrigeration machine. The high-pressure airflow supplied by the compressor 1 enters the reciprocating piston 10 located in the cylinder 13 via the gas distribution mechanism RV (gas distribution valve 6 and rotary valve 7), where it exchanges heat with the cold storage material 10c. Then, it expands in the expansion chamber 9, passes through the piston 10 again, exits the gas distribution mechanism, and returns to the low-pressure chamber of the compressor 1. Through this continuous cycle, a cooling effect is achieved.

[0003] The planar rotary valve comprises two main components: a rotary valve 7 and a distribution valve 6. One component is made of wear-resistant resin, while the other is made of metal. During operation, the two components are in planar contact. Rotation of the rotary valve 7 switches the connection between the channels on the rotary valve 7 and the distribution valve 6, thus switching between high and low pressure airflow. This contact is achieved through the pressure difference across the distribution mechanism. Then, for GM refrigeration units, the distribution mechanism (RV) is as follows... Figure 2 As shown, the high-pressure groove 72 and low-pressure port 71 on the rotary valve 7 are airtightly connected to the high-pressure airflow and the low-pressure airflow, respectively, and are eccentrically arranged on both sides of the rotary valve 7's own rotation axis O (dashed line). Within one cycle, the pressure between the switching surface 73 and the air distribution valve surface 61 is "asymmetric pressure," meaning that the pressure on both sides symmetrical about the rotation axis O is not equal. Therefore, this type of valve is called an asymmetric planar rotary valve.

[0004] The high-pressure gas discharged from compressor 1 acts on the back side of the valve face 61 opposite to the valve face 6. The valve face 6, relying on the positive pressure on its back side and the elastic force of spring 15, tightly adheres to the rotary valve 7, forming an airtight sliding contact surface. This ensures that the switching surface 73 of the asymmetrical rotary valve 7 and the valve face 61 of the valve face 6 will not be forced open by the gas pressure (the area on the sliding surface where pressure from both sides is applied is called the dual-action area). However, numerous practical operating cases have shown that in a structure where the working high-pressure gas and spring 15 symmetrically press the back side of the valve face 6 (opposite to the valve face 61) with respect to the central axis, the aforementioned "asymmetrical pressure" generates torque in the dual-action area. This torque makes the dual-action area closer to the high-pressure groove 72 side of the rotary valve 7 more prone to separation, posing a risk of refrigerant gas leakage.

[0005] To be specific, Figure 3 Taking the example shown, the rotary valve 7 is installed in the bearing 14 and presses against the distribution valve 6 coaxially with its own rotation axis O. The high-pressure groove 72 on the rotary valve 7 extends from the center of the rotation axis O along the direction away from the central axis O, and communicates with the opening—the high-pressure air hole 62—on the central axis of the distribution valve 6. The pressure of the high-pressure working gas is applied to each end and groove of the high-pressure air hole 62. The distribution valve 6 has a distribution valve air hole 63 machined on the side closer to the vent of the housing, centered on the rotation axis O. Since the high-pressure groove 72 and the low-pressure hole 71 on the rotary valve 7 are distributed on both sides of the rotation axis O, when the rotary valve 7 rotates around the O axis, the high-pressure groove 72, the low-pressure hole 71, and the distribution valve air hole 63 on the rotary valve 6 periodically overlap and separate. This method achieves the switching of high and low pressure valves for refrigerant flow.

[0006] by Figure 3 Taking the position as an example, the high-pressure groove 72 on the rotary valve 7 is divided into two regions X1 and X2 at the bottom of the groove with the central axis O as the boundary. A positive pressure Ph (high-pressure) is applied to these regions, and X1 > X2. Furthermore, at this moment, a lateral offset force in region X3 acts on the valve distribution surface 63, which easily causes the valve distribution valve 6 and the rotary valve 7 to move in the correct direction. Figure 3 The separation shown indicates a refrigerant leak, which affects performance. Summary of the Invention

[0007] The purpose of this invention is to address the problems existing in the prior art by providing a valve structure that can suppress leakage and a refrigeration machine using the valve structure. The refrigeration machine switches the flow path by rotating a rotary valve and using a gas distribution valve, and can suppress gas leakage between valves and ensure the stability of the equipment.

[0008] The purpose of the present invention is to be solved by the following technical solutions:

[0009] A valve structure capable of suppressing leakage includes a distribution valve and a rotary valve. The distribution valve is provided with a high-pressure air hole and a distribution valve air hole, and the rotary valve is provided with a low-pressure air hole and a high-pressure groove. The characteristic is that: the distribution valve surface of the distribution valve has at least one groove, which is arranged on the distribution valve surface within an annular area defined by a first envelope S1 formed by the radial maximum circumference of the high-pressure groove rotating relative to the rotation axis O and a second envelope S2 determined by the outer periphery of the smaller diameter component in the switching plane between the distribution valve surface and the rotary valve. At least one of the grooves is located on a semicircular surface of the distribution valve surface away from the distribution valve air hole and does not exceed the range of the semicircular surface.

[0010] The groove, high-pressure groove, high-pressure air hole, and air distribution valve air hole are never spatially overlapping, and the groove is not spatially connected to the outside of the valve structure; when the high-pressure groove on the rotary valve rotates to the fan-shaped area constructed by the groove on the air distribution valve surface, the groove is not connected to the low-pressure hole on the rotary valve.

[0011] The included angles α and β formed between the lines connecting the two ends of the groove to the rotation axis O and the axis O” of the line connecting the line O' which is perpendicular to both the rotation axis O and the reciprocating motion direction of the piston, respectively, both satisfy the following: greater than 0° and less than 90°.

[0012] The included angles α and β both satisfy the condition that they are greater than 10° and less than 70°.

[0013] The included angles α and β both satisfy the condition that they are greater than 20° and less than 50°.

[0014] The depth requirement of the groove is implemented in the following manner: the smaller of the minimum distance between the outer side of the groove and the second envelope S2 and the minimum distance between the inner side of the groove and the first envelope S1 is used as the reference size value, and the depth of the groove is not less than 1 / 10 of the reference size value.

[0015] The groove can be arc-shaped, straight, zigzag, or perforated.

[0016] When the first envelope S1 is smaller than the third envelope S3 formed by the radial maximum circumference of the outer edge of the low-pressure orifice rotating relative to the rotation axis O, and the slots are arranged on the valve surface within the annular area defined between the third envelope S3 and the second envelope S2, if there are two slots on the valve surface, the sector angle corresponding to any slot is less than 180°; if there are three slots on the valve surface, the sector angle corresponding to any slot is less than 120°; and if there are four slots on the valve surface, the sector angle corresponding to any slot is less than 90°.

[0017] When the valve face has three slots, the sector angle corresponding to any slot is less than 100°.

[0018] A refrigeration unit is disclosed, comprising the aforementioned valve structure. The refrigeration unit is a GM refrigeration unit, a pulse tube refrigeration unit, or a Solvin refrigeration unit. Specifically, the refrigeration unit includes a cylinder and a piston that reciprocates axially within the cylinder. The hot end of the piston forms a volume-changing hot cavity with the housing, and the cold end forms an expansion cavity with the cylinder. The piston is driven by a connecting rod, and guide sleeves are coaxially and tightly fitted at both ends of the connecting rod. A distribution valve is installed within the housing, and its rotational movement around its own axis is restricted by a distribution valve positioning pin. A rotary valve is mounted on a bearing and coaxially and tightly pressed against the distribution valve along its axis. The high-pressure air hole on the center line of the distribution valve is airtightly connected to the high-pressure airflow discharged from the compressor and the high-pressure groove with radial extension on the rotary valve on the center side corresponding to the rotating shaft O; the through hole—the low-pressure hole—machined on the other side of the rotary valve in the radial direction opposite to the high-pressure groove is always airtightly connected to the low-pressure passage; with the line O' connecting the reciprocating motion direction of the piston, the air hole of the distribution valve on the distribution valve is airtightly connected to the air hole of the cover and the hot cavity on the side of the rotating shaft O near the hot cavity.

[0019] The present invention has the following advantages over the prior art:

[0020] The valve structure of this invention, through the setting of a "gas path trap," causes leaked refrigerant gas to fall out of the "gas path trap" when it flows through the groove on the gas distribution valve surface. This prolongs the gas passage, slows down the leakage rate of high-pressure gas, and effectively reduces the risk of high-pressure refrigerant gas leaking from the valve into the surrounding low-pressure environment. Refrigeration machines using this valve structure switch flow paths by rotating the rotary valve and the gas distribution valve, which can suppress gas leakage between valves and ensure the stability of the equipment. Attached Figure Description

[0021] Figure 1 is a schematic diagram showing the structure of the cryogenic refrigerator in this invention;

[0022] Figure 2 is a three-dimensional structural diagram of a traditional valve.

[0023] Figure 3 is a schematic diagram of the leakage planar structure of a traditional valve;

[0024] Figure 4 is a cross-sectional schematic diagram of the valve structure provided by the present invention;

[0025] Figure 5 is a top view of the valve structure provided by the present invention;

[0026] Figure 6 is a schematic diagram illustrating the working effect of the valve structure provided by the present invention;

[0027] Appendix Figure 7 This is one of the schematic diagrams of a modified valve structure provided by the present invention;

[0028] Appendix Figure 8 This is the second schematic diagram of a modified valve structure provided by the present invention.

[0029] Wherein: 1—Compressor; 1a—High-pressure exhaust pipe; 1b—Low-pressure intake pipe; 2—Cover; 21—Cover air hole; 22—Low-pressure passage; 3—Cam; 31—Eccentric cam handle; 4—Guide sleeve; 5—Connecting rod; 6—Distribution valve; 61—Distribution valve face; 62—High-pressure air hole; 63—Distribution valve air hole; 7—Rotary valve; 71—Low-pressure hole; 72—High-pressure groove; 73—Switching plane; 74—Insertion hole; 75—Back side; 8—Hot chamber; 9—Expansion chamber; 10—Push piston; 10a—Piston front hole; 10b—Piston rear hole; 10c—Cold storage material; 11—Groove; 12—Motor; 13—Cylinder; 14—Bearing; 15—Spring; 16—Distribution valve positioning pin. Detailed Implementation

[0030] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0031] like Figure 1 As shown: Figure 1 As shown, this type of refrigeration machine includes a compressor 1, a housing 2, a cylinder 13, and a push piston 10. The housing 2 houses a motor 12 and a driving cam 3. An eccentric cam shank 31 on the cam 3 drives a connecting rod 5 to convert rotational motion into reciprocating motion, thereby driving the push piston 10 to move up and down within the cylinder 13. The gas distribution mechanism RV consists of a gas distribution valve 6 and a rotary valve 7. The gas distribution valve 6 is installed inside the housing 2, fixed within it by a gas distribution valve positioning pin 16, and coaxially arranged with the rotary valve 7. The cam shank 31 drives the rotary valve 7, mounted on a bearing 14, to rotate along the rotation axis. The compressor 1 draws in refrigerant gas, compresses it, and discharges it as high-pressure refrigerant gas. The high-pressure exhaust pipe 1a supplies high-pressure refrigerant gas to the housing 2 and transmits it through a high-pressure port 62 on the central axis of the gas distribution valve 6 to a high-pressure groove 72 on the rotary valve 7, which is airtightly fitted to it. The high-pressure groove 72 is not connected to the low-pressure port 71. The rotary valve 7 has a low-pressure port 71, which is connected to the low-pressure passage 22 inside the housing 2. The high-pressure groove 72 extends radially outward along the rotation axis O and is eccentrically arranged on the rotary valve 7. The low-pressure port 71 is arranged opposite the high-pressure groove 72 on the other side of the rotation axis O.

[0032] As shown in Figure 1, the low-pressure port 71 overlaps and connects with the air distribution valve port 63 on the air distribution valve 6. At this moment, the low-pressure port 71 on the rotary valve 7, the air distribution valve port 63 on the air distribution valve 6, and the hood port 21 on the hood 2 are connected. The system is in the low-pressure exhaust stage. The gas in the expansion chamber 9 changes from high pressure to low pressure and flows out sequentially through the piston rear port 10b on the push piston 10, the cold storage material 10c, and the piston front port 10a, returning to the low-pressure suction pipe 1b of the compressor 1. When the rotary valve 7 rotates a certain angle, the low-pressure port 71 is no longer connected to the air distribution valve port 63 on the air distribution valve 6. Instead, the high-pressure groove 72 on the rotary valve 7 is connected to the air distribution valve port 63 on the air distribution valve 6 (this connection is not shown). At this moment, the high-pressure gas discharged from the compressor 1 enters the cylinder 13 through the high-pressure port 62 on the air distribution valve 6 and the high-pressure groove 72 on the rotary valve 7 connected to it. It then sequentially passes through the piston front hole 10a, the cold storage material 10c, and the piston rear hole 10b on the push piston 10 and enters the expansion chamber 9. During the above process, the high-pressure gas discharged from the compressor 1 acts on the back of the air distribution valve 6. The air distribution valve 6, relying on the positive pressure on the back and the elastic force of the spring 15, tightly fits against the rotary valve 7 to form an airtight sliding contact surface. Both the rotary valve 7 and the air distribution valve 6 are designed as rotating bodies along the rotation axis. The rotary valve 7 is rotatably supported in the housing 2 by the bearing 14. The air distribution valve 6 is coaxially arranged in the housing 2 with the rotary valve 7. The air distribution valve 6 is fixed by the air distribution valve positioning pin 16 so that it cannot rotate, but can be installed and removed along the axial direction of the rotation axis O.

[0033] The following is in conjunction with the appendix Figure 4 , Figure 5 , Figure 6 , Figure 7 , Figure 8 The valve structure capable of suppressing leakage provided by the present invention will be further illustrated with specific embodiments.

[0034] Example 1

[0035] by Figure 4 , Figure 5 , Figure 6 Taking an example, the valve structure provided by the present invention will be described in detail.

[0036] A second envelope S2 is formed by the outer diameter of the smaller component in the contact surface between the valve 6 and the rotary valve 7, and a first envelope S1 is formed by the radially largest circumference formed by the high-pressure groove 72 of the valve 7 moving along the rotation axis O. An annular region coaxial with the rotation axis O is formed between the first envelope S1 and the second envelope S2. Within this corresponding annular region, at least one groove 11 is present on the valve surface 61 of the valve 6.

[0037] The axis O” is set perpendicular to the line O' connecting the rotation axis O and the reciprocating motion direction of the push piston 10, dividing the valve surface 61 of the valve 6 into two regions: “upper” and “lower”.

[0038] The air distribution valve orifice 63 of the air distribution valve 6 is closer to the hot cavity 8 on the line O' connecting the reciprocating motion direction of the piston 10, and is located "below" the axis O”. The groove 11 is arranged on the other side of the axis O”, opposite to the air distribution valve orifice 63, and is "above" the axis O” in the direction shown in the figure.

[0039] When the rotary valve 7 moves to Figure 4 , Figure 5 At this position, the low-pressure port 71 on the rotary valve 7 is connected to the gas port 63 of the distribution valve. Under the back pressure of the distribution valve 6, the area below the axis "O" is under a relatively high pressure. At the same time, due to the eccentric effect of the high pressure in the high-pressure groove 72 on the rotary valve 7 on the distribution valve surface 61 of the distribution valve 6, one end of the valve structure is close to the other, while the other end is separated. This causes refrigerant gas to leak out from the high-pressure groove 72 along the slightly open contact surface.

[0040] According to the described implementation scheme, the slot 11 is arranged in the outer region of the high-pressure slot 72. Its width and depth are much larger than the slightly open dimensions mentioned above, forming an "air path trap," such as... Figure 6 As indicated by the arrow in the diagram, the leaked refrigerant gas flow falls into the "gas path trap" as it passes through the tank 11, which prolongs the gas path, slows down the leakage rate of the high-pressure gas flow, and reduces the risk of high-pressure refrigerant leaking into the surrounding low-pressure environment.

[0041] by Figure 5 The top view of the valve structure shown is used as an example for detailed explanation.

[0042] The dashed line represents the structure of the rotary valve 7, and the thick solid line represents the structure of the distribution valve 6. When the distribution valve 6 and the rotary valve 7 are in contact, the outer circumference of the distribution valve 6 is smaller; therefore, the outer circumference of the distribution valve 6 (the outer circumference of the distribution valve surface 61) is used as the second envelope S2. The high-pressure groove 72, extending radially outward from the central axis of the rotary valve 7, forms the first envelope S1 around the rotation axis O. The central axis of the distribution valve 6 has a high-pressure air hole 62 that is airtightly connected to the center side of the high-pressure groove 72. Below the axis O”, there is a distribution valve air hole 63 connecting to the hot cavity 8. An arc-shaped groove 11 is arranged above the axis O”, that is, in the direction opposite to the distribution valve air hole 63 relative to the rotation axis O. The groove 11 is arranged outside the first envelope S1 and inside the second envelope S2. Therefore, within a week, the slot 11 never overlaps with the high-pressure slot 72 of the rotary valve 7 in terms of spatial position, nor with the high-pressure air hole 62 or the air hole 63 on the air distribution valve 6.

[0043] Based on the above structure, the inner edge of the groove 11 on the radial side closest to the rotation axis O never overlaps with the high-pressure groove 72 at any time. That is, the shortest distance between the farthest radial end of the high-pressure groove 72 and the inner edge of the groove 11 (e.g., Figure 5 As shown), a first airtight path is formed; and the shortest distance between the outer edge of the groove 11 and the second envelope S2 forms a second airtight path.

[0044] When the valve is Figure 5 In the indicated state, when the high-pressure tank 72 is slightly open at its radially distal end, the high-pressure refrigerant, passing through the first airtight path, has a recessed space in tank 11 that is much larger than the opening size of the first airtight path, thus forming an airtight "gas path trap." This causes leaking refrigerant to rush into the recessed space of tank 11, resulting in a slowdown in flow rate. Since tank 11 does not overlap with the second envelope S2, i.e., it is not connected to the outside of the valve, the leaking refrigerant must "climb up" from the "gas path trap" and enter the second airtight path. Because the opening size of the second airtight path is much smaller than the recessed space of tank 11, an "air plug" phenomenon is formed, preventing the leaking refrigerant from overflowing into the space outside the valve.

[0045] In this embodiment, due to the limited space of the valve structure, the angles α and β formed by the lines connecting the two ends of the groove 11 to the center of the valve surface 61 and the line O' perpendicular to both the rotation axis O and the reciprocating motion direction of the piston 10 are greater than 0° and less than 90°. That is, the arc-shaped groove 11 is on the upper semicircular surface of the valve surface 61, ensuring that when the rotary valve 7 rotates, the high-pressure groove 72 enters the fan-shaped area of ​​the groove 11 relative to the rotation axis O at an angle of 180° - α - β°, and the low-pressure hole 71 does not enter this area, thus avoiding the indirect communication between the high-pressure groove 72 and the low-pressure hole 71 through the groove 11 during the rotation of the rotary valve 7, which would otherwise cause internal air leakage.

[0046] Furthermore, both the included angles α and β are greater than 10° and less than 70°.

[0047] To elaborate further, both the included angles α and β are greater than 20° and less than 50°.

[0048] In the implementation of the solution provided in this embodiment, the low-pressure port 71 on the rotary valve 7 may overlap with the first envelope S1. Figure 5 (As shown). That is, during a switching cycle, a portion of the time slot 11 and the low-pressure port 71 overlap spatially, forming a low-pressure airflow communication state.

[0049] Example 2

[0050] by Figure 7 For example, groove 11 can be straight, broken, or perforated.

[0051] This invention is not limited to the above-described embodiments. Various design changes and modifications are possible, and such modifications are also within the scope of this invention, as will be obvious to those skilled in the art.

[0052] Example 3

[0053] by Figure 8 For example, there are three grooves 11 on the valve face 61. In this embodiment, one side of the groove 11 is arranged according to the limitation of Embodiment 1, and the other two grooves 11 are arranged on both sides of the valve face 61 within the annular area defined between the third envelope S3 and the second envelope S2, or all three grooves 11 are arranged on the valve face 61 within the annular area defined between the third envelope S3 and the second envelope S2. The typical layout is implemented according to a symmetrical structure. And the sector angle corresponding to each groove 11 is less than 120°, and more preferably less than 100°. The inner edge of the groove is outside the envelope of the farthest radial distance between the high-pressure groove 72 and the low-pressure hole 71, that is, outside the third envelope S3, and does not overlap with the high-pressure groove 72 on the rotary valve 7 and the high-pressure air hole 62 and the air hole 63 on the valve 6 in spatial position, so that it can still suppress valve leakage.

[0054] A refrigeration unit employing the aforementioned valve mechanism includes the valve mechanism, wherein the gas distribution valve 6 of the valve mechanism is eccentrically fixed to the housing 2 by a valve body positioning pin 16; the rotary valve 7 of the gas distribution mechanism is positioned inside the housing 2 by a bearing 14. This refrigeration unit is any type of valve-switching refrigeration unit, not limited to Gifford-McMahon refrigeration units, Solvin refrigeration units, pulse tube refrigeration units, etc. A groove 11 is provided on the gas distribution valve surface 61 (i.e., the pressure zone where separation and gas leakage are likely to occur) at the far end of the high-pressure groove 72 of the rotary valve 7 away from the gas distribution valve orifice 63 to intercept leaked refrigerant gas, effectively suppressing leakage.

[0055] The above embodiments are merely illustrative of the technical concept of the present invention and should not be construed as limiting the scope of protection of the present invention. Any modifications made to the technical solutions based on the technical concept proposed in this invention shall fall within the scope of protection of this invention. Technologies not covered in this invention can be implemented using existing technologies.

Claims

1. A valve structure capable of suppressing leakage, comprising a gas distribution valve (6) and a rotary valve (7), wherein the gas distribution valve (6) is provided with a high-pressure air hole (62) and a gas distribution valve air hole (63), and the rotary valve (7) is provided with a low-pressure hole (71) and a high-pressure groove (72), characterized in that: The gas distribution valve (6) has at least one groove (11) on its surface (61). The groove (11) is arranged on the gas distribution valve surface (61) in an annular region defined between a first envelope S1 formed by the radial maximum circumference formed by the rotation of the high-pressure groove (72) relative to the rotation axis O and a second envelope S2 determined by the outer circumference of a smaller diameter component in a switching plane (73) of the rotary valve (7). At least one of the grooves (11) is located on a semicircular surface of the gas distribution valve surface (61) away from the gas distribution valve air hole (63). and does not exceed the range of the semicircular surface; the groove (11) and the high-pressure groove (72) and the high-pressure air hole (62) and the air distribution valve air hole (63) do not overlap in spatial position, and the groove (11) is not connected to the outside of the valve structure in spatial position; when the high-pressure groove (72) on the rotary valve (7) rotates to the fan-shaped area constructed by the groove (11) on the air distribution valve surface (61), the groove (11) is not connected to the low-pressure hole (71) on the rotary valve (7); the shape of the groove (11) is arc-shaped, straight-line-shaped, or broken-line-shaped.

2. The valve structure capable of suppressing leakage according to claim 1, characterized in that: The angles α and β formed between the lines connecting the two end edges of the groove (11) and the rotation axis O and the axis O" which is perpendicular to the line O' connecting the rotation axis O and the reciprocating motion direction of the push piston (10) respectively satisfy the following requirements: greater than 0° and less than 90°.

3. The valve structure capable of suppressing leakage according to claim 2, characterized in that: The angles α and β both satisfy: greater than 10° and less than 70°.

4. The valve structure capable of suppressing leakage according to claim 3, characterized in that: The angles α and β both satisfy: greater than 20° and less than 50°.

5. The valve structure capable of suppressing leakage according to claim 1, characterized in that: The depth requirement of the groove (11) is implemented in the following manner: the smaller dimension value of the minimum distance between the outer side of the groove (11) and the second envelope S2 and the minimum distance between the inner side of the groove (11) and the first envelope S1 is used as a reference dimension value, and the depth of the groove (11) is not less than 1 / 10 of the reference dimension value.

6. The valve structure capable of suppressing leakage according to claim 1, characterized in that: When the first envelope S1 is smaller than a third envelope S3 formed by a radial maximum circumference formed by the outer edge of the low-pressure hole (71) rotating relative to the rotation axis O, and the groove (11) is arranged on the valve surface (61) in an annular area defined between the third envelope S3 and the second envelope S2, if two grooves (11) are provided on the valve surface (61), the fan angle corresponding to any groove (11) is less than 180°, if three grooves (11) are provided on the valve surface (61), the fan angle corresponding to any groove (11) is less than 120°, and if four grooves (11) are provided on the valve surface (61), the fan angle corresponding to any groove (11) is less than 90°.

7. The valve structure capable of suppressing leakage according to claim 6, characterized in that: When three grooves (11) are provided on the gas distribution valve surface (61), the sector angle corresponding to any groove (11) is less than 100°.

8. A refrigerator, characterized in that: The refrigerator has the valve structure described in any one of claims 1 to 7, and the refrigerator is a GM refrigerator, a pulse tube refrigerator or a Solvang refrigerator.

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