CN113124588B - Valve mechanism and ultralow temperature refrigerator comprising same - Google Patents
Valve mechanism and ultralow temperature refrigerator comprising same Download PDFInfo
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- CN113124588B CN113124588B CN202110514389.1A CN202110514389A CN113124588B CN 113124588 B CN113124588 B CN 113124588B CN 202110514389 A CN202110514389 A CN 202110514389A CN 113124588 B CN113124588 B CN 113124588B
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- outflow port
- pressure gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
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- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Multiple-Way Valves (AREA)
Abstract
The invention discloses a valve train and an ultralow temperature refrigerator comprising the same, wherein the valve train comprises a high-pressure gas inflow port (20), a valve air hole (21), a rotary valve concave part (31) and a low-pressure gas outflow port (32), the front section area of the rotary valve concave part (31) can be overlapped with the valve air hole (21), and the section width of the front section area of the rotary valve concave part (31) gradually increases from the front end to the rear end of the rotary valve concave part (31); the entire area of the low-pressure gas outflow port (32) can be overlapped with the gas distribution valve gas hole (21), and the cross-sectional width of the front section area of the low-pressure gas outflow port (32) gradually increases from the front end to the rear end of the low-pressure gas outflow port (32). The ultralow temperature refrigerator is provided with the valve train, a compressor and an expander. The valve mechanism can prevent the abrupt change of mass flow, reduce the irreversible loss of gas working medium through the rotary valve and improve the efficiency of the refrigerator.
Description
Technical Field
The invention belongs to the technical field of ultralow temperature refrigerators, and particularly relates to a valve mechanism capable of improving mass flow passing through a rotary valve and pressure waves in an expander and improving the efficiency of the refrigerator and an ultralow temperature refrigerator comprising the valve mechanism.
Background
Since the GM refrigerator of the Gifford invention in the united states of america of the 20 th century 60 s, it has been developed for many years and has been widely used in the fields of low-temperature electronic device magnetizers, low-temperature medicine, and the like. GM refrigerators generally include a two-part expander and a compressor. The expander drives a pushing piston that reciprocates in the axial direction, and a regenerator built in the pushing piston, usually by a driving mechanism. The pusher piston is accommodated in a cylinder guiding its reciprocating movement. By means of the relative movement of the pushing piston and the cylinder, a variable volume can be formed between the cylinder and the pushing piston, which serves as an expansion space for the working gas. The working gas volume change and the pressure change of the expansion space have proper phase difference, and the expansion space can generate cold energy.
The common characteristics of the Gift-Maxwell (GM) refrigerator, the GM pulse tube refrigerator and the Sol refrigerator are that a gas distribution valve is adopted to control the inlet and outlet of working fluid, and the gas inlet of the high-pressure working gas from the compressor to the expander and the gas return of the low-pressure working gas from the expander to the compressor are alternately switched.
The abrupt opening and closing of the valve can lead to the severe fluctuation of the air flow in the expander, and the working medium gas has huge irreversible loss in the rotary valve, thereby increasing the input power consumption of the compressor and reducing the efficiency of the ultralow temperature refrigerator.
Disclosure of Invention
The invention aims at solving the problems in the prior art and provides a valve mechanism capable of improving mass flow passing through a rotary valve and pressure waves in an expander and improving the efficiency of the refrigerator and an ultralow temperature refrigerator comprising the valve mechanism, and the ultralow temperature refrigerator comprising the valve mechanism can reduce irreversible loss of the ultralow temperature refrigerator.
The invention aims at solving the problems through the following technical scheme:
the utility model provides a valve train, includes the distributing valve that is equipped with high-pressure gas inflow port and distributing valve gas pocket and is equipped with rotary valve concave part and low-pressure gas outflow port's rotary valve, its characterized in that: the front section area of the rotary valve concave part can be overlapped with the air distribution valve air hole, so that the rotary valve concave part is in fluid connection with the air distribution valve air hole, and the section width of the front section area of the rotary valve concave part gradually increases from the front end to the rear end of the rotary valve concave part; the entire area of the low-pressure gas outflow port can overlap with the gas distribution valve gas hole so that the low-pressure gas outflow port is fluidly connected with the gas distribution valve gas hole, and the sectional width of the front section area of the low-pressure gas outflow port gradually increases from the front end to the rear end of the low-pressure gas outflow port.
The contour line of the front section area of the rotary valve concave part is a curve; the contour line of the front section area of the low-pressure gas outflow port is a curve.
The outer edge contour line of the front section area of the rotary valve concave part is inscribed on the inner edge of the outer edge contour line of the air hole of the distributing valve.
And the middle section contour line and the rear section contour line of the low-pressure gas outflow port are overlapped with the corresponding contour lines of the gas distributing valve gas hole.
The contour line of the rotary valve concave part comprises a concave part semicircular arc at the rear section, a concave part first straight line and a concave part second straight line at the middle section, a concave part first arc and a concave part second arc at the front section, and the concave part semicircular arc, a concave part second straight line at the outer side, a concave part first arc at the outer side, a concave part second arc at the inner side and a concave part first straight line at the inner side are sequentially connected end to form the contour line of the rotary valve concave part.
The contour line of the low-pressure gas outflow port comprises an outflow port semicircular arc at the rear section, an outflow port inner circular arc and an outflow port outer circular arc at the middle section, an outflow port first circular arc and an outflow port second circular arc at the front section, and the outflow port semicircular arc, an outflow port outer circular arc at the outer side, an outflow port first circular arc at the outer side, an outflow port second circular arc at the inner side and an outflow port inner circular arc at the inner side are sequentially connected end to form the contour line of the low-pressure gas outflow port; the inner arc line of the outflow opening and the outer arc line of the outflow opening have the same central angle.
The air hole of the air distributing valve is an annular elliptical groove, and the contour line of the air hole of the air distributing valve is composed of a first semicircular arc of the air hole, an outer circular arc of the air hole, a second semicircular arc of the air hole and an inner circular arc of the air hole which are connected end to end in sequence.
In a first phase of the rotation direction of the rotary valve, the concave part of the rotary valve is connected with the air hole of the air distributing valve at a first opening degree, and gradually changes from the first opening degree to a second opening degree, wherein the first opening degree is smaller than the second opening degree; in a third phase of the rotary valve rotation direction, the rotary valve recess is separated from the air distribution valve air hole.
In a fourth phase of the rotation direction of the rotary valve, the low-pressure gas outflow port is in fluid connection with the gas distributing valve gas hole at a third opening degree, and gradually changes from the third opening degree to a fourth opening degree, wherein the third opening degree is smaller than the fourth opening degree; in a sixth phase of the rotary valve rotation direction, the low-pressure gas outflow port is separated from the gas distribution valve gas hole.
An ultralow temperature refrigerator comprises the valve train, a compressor and an expander, wherein the compressor is provided with a working gas outlet and a working gas inlet; the expander is provided with a low-pressure gas chamber, the gas expansion space of which is communicated with the working gas inlet; the distribution valve in the distribution mechanism is fixed in the low-pressure gas chamber, and is provided with a stator plane perpendicular to a valve rotating shaft, a high-pressure gas inflow port which is opened on the stator plane and is communicated with a working gas discharge port of the compressor, and a distribution valve air hole which is opened on the stator plane and is communicated with the gas expansion space; the rotary valve in the valve train is disposed in the low-pressure gas chamber and rotates about a rotation axis relative to the valve train, and the rotary valve includes a rotor plane perpendicular to the rotation axis and in contact with the stator plane, a rotary valve recess opening in the rotor plane and communicating with the high-pressure gas inlet, and a low-pressure gas outlet.
Compared with the prior art, the invention has the following advantages:
the valve mechanism can enable the internal mass flow passing through the rotary valve to be approximately sinusoidal, prevent the sudden change of the mass flow, reduce the irreversible loss of the gas working medium passing through the rotary valve and improve the efficiency of the refrigerator.
The rotary valve concave part and partial contour line of the low-pressure gas outflow opening in the valve mechanism are formed by circular arcs, so that the opening degree of air inlet and air outlet of the refrigerator is gradually and slowly increased, the severe fluctuation of the gas pressure in the expander is reduced, the change of the air flow is gentle, and the performance of the heat regenerator is improved.
Drawings
Fig. 1 is a block diagram schematically showing an entire structure of an ultralow temperature refrigerator according to an embodiment of the present invention;
FIG. 2 is an exploded perspective view schematically illustrating a valve train according to an embodiment of the present invention;
FIG. 3 is a top view schematically illustrating a rotary valve according to one embodiment of the present invention;
FIG. 4 is a top view schematically illustrating a gas distribution valve according to an embodiment of the present invention;
FIG. 5 is a schematic diagram illustrating a method of determining a contour of a rotary valve recess according to an embodiment of the present invention;
fig. 6 is a diagram schematically showing a method of determining a contour line of a low-pressure gas outflow port according to an embodiment of the present invention;
FIG. 7 schematically illustrates a valve phase diagram of a rotary valve and a distribution valve according to one embodiment of the present invention as the rotary valve rotates;
fig. 8 schematically shows a graph of the mass flow, pressure wave and piston travel versus rotary valve phase for a cryocooler according to an embodiment of the present invention.
Wherein: 1-a compressor; 11-a working gas outlet; 12-working gas inlet; 2-valve mechanism; 2 a-an air distributing valve; 2 b-rotary valve; 3-a low pressure gas chamber; 4-a housing gas flow path; 5-a connecting rod; 6-a top cap gas flow path; 7-a heat regenerator; 8, an air cylinder; 9-pushing the piston; 10-a cold end heat exchanger; 18-stator plane; 19-rotor plane; 20-a high pressure gas inlet; 21-distributing valve air holes; 21 a-a first semicircular arc of air holes; 21 b-a second semicircular arc of air holes; 21 c-pore inner arc line; 21 d-an air hole outer arc line; 31-a rotary valve recess; 31 a-recess first arc; 31 b-a concave second arc; 31 c-a first straight line of concave parts; 31 d-concave semicircular arc; 31 e-concave second line; 32-a low pressure gas outflow port; 32 a-outflow semicircular arc; 32 b-an arc within the outflow opening; 32 c-the first arc of outflow opening; 32 d-outflow opening outer arc line; 32 e-the second arc of outflow opening.
Detailed Description
The invention is further described below with reference to the drawings and examples.
As shown in fig. 1: an ultra-low temperature refrigerator, the ultra-low temperature refrigerator comprising: a compressor 1, an expander, and a valve train, wherein the compressor 1 is provided with a working gas outlet 11 and a working gas inlet 12; a low-pressure gas chamber 3 having a gas expansion space communicating with the working gas inlet 12; the distributing valve 2a in the distributing mechanism is fixed to the low-pressure gas chamber 3, and the distributing valve 2a is provided with a stator plane 18 perpendicular to the valve rotation axis, a high-pressure gas inflow port 20 which is opened in the stator plane 18 and is communicated with the working gas discharge port 11 of the compressor 1, and a distributing valve air hole 21 which is opened in the stator plane 18 and is communicated with the air cylinder 8; the rotary valve 2b in the valve train is rotatably supported in the low-pressure gas chamber 3 about a valve rotation axis with respect to the valve train 2a, the rotary valve 2b includes a rotor plane 19 perpendicular to the rotation axis and in contact with the stator plane 18, a rotary valve concave portion 31 opened in the rotor plane 19 and separated from each other, and a low-pressure gas outflow port 32, and the rotary valve concave portion 31 can communicate with the high-pressure gas inflow port 20; the distributing valve 2a is fixed, the rotor plane 19 of the rotary valve 2b rotates and slides relative to the stator plane 18, and the rotor plane 19 is closely contacted with the stator plane 18, so that the leakage of working gas can be prevented.
The working engineering of the G-M refrigerator is briefly described as follows: at the beginning, the control mechanism makes the piston 9 at the bottom of the cylinder 8, and at the same time, the high-pressure working gas from the compressor 1 enters the expander through the gas pipeline 11a, the distributing valve 2a is fixed, the rotary valve concave part 31 is in the air inlet phase, enters the top cover gas flow path 6 through the shell gas flow path 4, further enters the heat regenerator 7, and the pressure of the heat regenerator 7 is increased. When the pressure is balanced, the pushing piston 9 moves upwards from the bottom of the cylinder 8, at the same time as the high-pressure gas cooled by the regenerator 7 enters the cold chamber. The pushing piston 9 moves to the top of the cylinder 8 and the intake ends. And a certain angle is formed between the air inlet phase and the air outlet phase, so that the air inlet valve and the air outlet valve are closed, and high-pressure and low-pressure air leakage is prevented. When the distributing valve 2a and the rotary valve 2b are in the exhaust phase, the gas of the cold chamber is communicated with the low-pressure gas chamber 3 through the regenerator 7. At this time, the high pressure gas in the cold chamber is discharged to the low pressure side, thereby obtaining cold energy, which is transferred out of the cold end heat exchanger 10. The gas is heated by the regenerator 7 and returned to the compressor 1. At the same time, the piston 9 is pushed back to the bottom of the cylinder 8 again, and the exhaust is ended. Thus, the whole system can continuously work and continuously acquire the cold energy from cycle to cycle.
As shown in fig. 2,3, 4, and 7, a valve train includes a valve 2a provided with a high-pressure gas inflow port 20 and a valve air vent 21, and a rotary valve 2b provided with a rotary valve concave portion 31 and a low-pressure gas outflow port 32, a front-stage region of the rotary valve concave portion 31 being capable of overlapping the valve air vent 21 so that the rotary valve concave portion 31 is fluidly connected to the valve air vent 21, a cross-sectional width of the front-stage region of the rotary valve concave portion 31 gradually increasing from a front end to a rear end of the rotary valve concave portion 31; the entire area of the low-pressure gas outflow port 32 can overlap with the gas distribution valve gas hole 21 such that the low-pressure gas outflow port 32 is fluidly connected to the gas distribution valve gas hole 21, and the sectional width of the front-stage area of the low-pressure gas outflow port 32 gradually increases from the front end to the rear end of the low-pressure gas outflow port 32. As shown in fig. 7, in a first phase of the rotary valve 2b in the rotation direction, the rotary valve concave portion 31 is connected to the air distribution valve hole 21 at a first opening degree and gradually changes from the first opening degree to a second opening degree, and the first opening degree is smaller than the second opening degree; in a third phase of the rotational direction of the rotary valve 2b, the rotary valve recess 31 is separated from the air distribution valve air hole 21; in a fourth phase of the rotation direction of the rotary valve 2b, the low-pressure gas outflow port 32 is fluidly connected with the gas distribution valve gas hole 21 at a third opening degree, and gradually changes from the third opening degree to a fourth opening degree, the third opening degree being smaller than the fourth opening degree; in the sixth phase of the rotary valve rotation direction, the low-pressure gas outflow port 32 is separated from the gas distribution valve gas hole 21.
In fig. 3, the contour line of the front region of the rotary valve concave portion 31 is curved, and the outer edge contour line of the front region of the rotary valve concave portion 31 is inscribed on the inner edge of the outer edge contour line of the distribution valve air hole 21. Specifically, the contour line of the rotary valve concave portion 31 includes a concave semicircular arc 31d at the rear stage, a concave first straight line 31c and a concave second straight line 31e at the middle stage, a concave first arc 31a and a concave second arc 31b at the front stage, and the concave semicircular arc 31d, the concave second straight line 31e at the outer side, the concave first arc 31a at the outer side, the concave second arc 31b at the inner side, and the concave first straight line 31c at the inner side are sequentially connected end to form the contour line of the rotary valve concave portion 31.
In fig. 3, the contour line of the front section area of the low-pressure gas outflow port 32 is curved, and the middle section contour line and the rear section contour line of the low-pressure gas outflow port 32 coincide with the corresponding contour lines of the gas distribution valve gas hole 21. Specifically, the contour line of the low-pressure gas outflow port 32 includes an outflow port semicircular arc 32a at the rear section, an outflow port inner circular arc 32b and an outflow port outer circular arc 32d at the middle section, an outflow port first circular arc 32c and an outflow port second circular arc 32e at the front section, and the contour line of the low-pressure gas outflow port 32 is formed by sequentially connecting the outflow port semicircular arc 32a, the outflow port outer circular arc 32d at the outer side, the outflow port first circular arc 32c at the outer side, the outflow port second circular arc 32e at the inner side and the outflow port inner circular arc 32b at the inner side end to end; the outflow-opening inner arc 32b and the outflow-opening outer arc 32d have the same central angle.
In fig. 4, the air distributing valve air hole 21 is an annular elliptical groove, the outline of the air distributing valve air hole 21 is composed of an air hole first semicircular arc 21a, an air hole outer circular arc 21d, an air hole second semicircular arc 21b and an air hole inner circular arc 21c which are connected end to end in sequence, the air hole outer circular arc 21d and the air hole inner circular arc 21c on the outer side are composed to have the same central angle, and the radius of the air hole first semicircular arc 21a and the air hole second semicircular arc 21b are the same.
A method of determining the contour of the rotary valve recess 31, the low pressure gas outlet 32 is provided below to further explain the valve train provided by the present invention.
As shown in fig. 5, the rotary valve recess 31 defines a contour of the rotary valve recess 31 on the rotor plane 19. The contour line of the rotary valve concave portion 31 is composed of a concave portion first circular arc 31a, a concave portion second circular arc 31b, a concave portion first straight line 31c, a concave portion semicircular arc 31d, and a concave portion second straight line 31e which are connected end to end in this order. The contour line of the rotary valve concave portion 31 in the present embodiment can be determined by that the center O 1 of the concave portion semicircular arc 31d is located at the center of the rotor plane 19 of the rotary valve 2b, and the radius is R 3; the concave first straight line 31c and the concave second straight line 31e intersect with an arc with a radius R 1 at G, D points from both end points of the concave semicircular arc 31 d; the first arc 31a of the concave part is tangent to the second straight line 31E of the concave part at the point D, and is tangent to the arc with the radius R 2 at the point F, and the end point is the point E; the straight line HE forms an included angle beta with the first straight line 31c of the concave part and has the same starting point H; the concave second arc 31b is tangent to the concave first straight line 31c at point G, and the end point is point E.
As shown in fig. 6, the low-pressure gas outflow opening 32 defines a contour of the outflow opening 32 on the rotor plane 19. The contour line of the low-pressure gas outflow port 32 is formed by sequentially connecting an outflow port semicircular arc 32a, an outflow port inner circular arc 32b, an outflow port second circular arc 32e, an outflow port first circular arc 32c and an outflow port outer circular arc 32d in an end-to-end manner. The inner arc line 32b of the outflow port and the outer arc line 32d of the outflow port have the same central angle, the inner diameter of the inner arc line 32b of the outflow port is R 1, the inner diameter of the outer arc line 32d of the outflow port is R 2, and R 2>R1 is arranged; the radius R 1 of the outflow opening inner arc line 32b is equal to the radius of the air hole inner arc line 21c on the air distribution valve 2a, and the radius R2 of the outflow opening outer arc line 32d is equal to the radius of the air hole outer arc line 21d on the air distribution valve 2 a. The outlet first circular arc line 32c and the outlet second circular arc line 32e of the low-pressure gas outlet 32 in the present embodiment can be determined by setting the center of the outlet first circular arc line 32c to B, the starting point to a, the radius to R 2-R1, and the angle α between the straight line AB and the perpendicular line passing through O 1; the center of the second circular arc 32e of the outflow port is O 1, the radius is R 1, the second circular arc intersects with the straight line AB at the point B, and the first circular arc of the outflow port intersects with the first circular arc of the outflow port at the point C.
The radius R 1、R2、R3 is determined by the sizes of the rotary valve 2b and the distributing valve 2a, and the angles alpha and beta are determined according to the distributing time sequence of the valve.
The above is only one contour line determining method of the present embodiment, and the progressive line and other curve contours having the same effects of the present invention are within the scope of the present invention.
The variation trend of mass flow, pressure wave and piston stroke in the ultralow temperature refrigerator adopting the valve mechanism provided by the invention along with the air inlet and outlet working procedures is shown in figure 8,
In the intake and exhaust process, the horizontal axis represents the rotational phase of the rotary valve 2b and the air distribution valve 2a, 0 ° represents the start time of a cycle, and 360 ° represents the end time of a cycle; the vertical axis indicates the overlapping area of the rotary valve concave portion 31 of the rotary valve 2b and the air distribution valve air hole 21 of the air distribution valve 2a, and the overlapping area of the low-pressure air outlet 32 of the rotary valve 2b and the air distribution valve air hole 21 of the air distribution valve 2a, that is, the intake and exhaust openings. The first opening and the third opening represent the start of air intake and exhaust, and the opening is 0; the second opening is the area enclosed by the first arc 31a of the concave part, the second arc 31b of the concave part and the inner arc 21c of the air hole, and is the variable air inlet opening which is gradually increased, maximum and gradually decreased; the fourth opening is the overlapping area of the low-pressure gas outflow port 32 and the gas distribution valve gas hole 21, and is the gradually increasing-maximum-gradually decreasing variable exhaust opening.
Fig. 8 schematically shows a comparison between an intake step a and an exhaust step c of an ultralow temperature refrigerator and an intake step b and an exhaust step d of a conventional ultralow temperature refrigerator according to the present invention. As shown in fig. 7, the valve phase change of the air distribution valve 2a and the rotary valve 2b when the rotary valve 2b rotates, the air intake step a ranges from the first phase θ 1 to the third phase θ 3 of the rotary valve 2b, the air exhaust step c ranges from the fourth phase θ 4 to the sixth phase θ 6 of the rotary valve 2b, the second phase θ 2 is the maximum air intake opening position where the air intake is at the second opening, and the fifth phase θ 5 is at the maximum air exhaust opening position where the air exhaust is at the fourth opening. The gas process a and the exhaust process c alternate with each other. Before the exhaust process c starts, the intake process a ends; and the exhaust process c ends before the intake process a begins.
Fig. 8 schematically shows the change in stroke of the piston 9 in the ultralow temperature refrigerator according to the intake and exhaust process. The intake starts before the pushing piston 9 reaches the bottom dead center; the exhaust starts before the piston 9 is pushed to the top dead center.
The first phase θ 1 to the second phase θ 2 correspond to the preceding part of the intake process a, and the intake opening is gradually increased, so that the mass flow through the rotary valve 2b is approximately sinusoidal; the second phase θ 2 to the third phase θ 3 are the main part of the intake process a. The fourth to fifth phases θ 4 to θ 5 correspond to the preceding part of the exhaust process c, and similarly, the internal mass flow curve passing through the rotary valve 2b is made to vary approximately sinusoidal, and the fifth to sixth phases θ 5 to θ 6 correspond to the main part of the exhaust process c.
The distributing valve 2a and the rotary valve 2b are matched through phase, so that the inflow and the discharge of the refrigerating gas are controlled. According to the embodiment provided by the invention, the outline of the leading part of the rotary valve concave part 31 of the rotary valve 2b is composed of a concave part first circular arc 31a and a concave part second circular arc 31b, so that the air inlet is gradually opened; the leading part profile of the low-pressure gas outflow port 32 of the rotary valve 2b is composed of an outflow port first circular arc line 32c and an outflow port second circular arc line 32e, so that the exhaust opening degree is gradually increased; the gradual opening of the intake and exhaust can improve the refrigerator efficiency by controlling the abrupt change of the mass flow of the rotary valve 2 b.
Fig. 8 schematically shows the pressure wave variation trend in the ultra-low temperature refrigerator. As can be seen from fig. 8, the pressure wave f in the conventional expander has a rectangular shape due to the opening and closing of the intake and exhaust air; the air inlet and the air outlet of the air conditioner are gradually opened, the pressure wave g is gentle, the air flow in the system is stable, and the efficiency of the air conditioner can be improved.
Fig. 8 schematically shows the trend of mass flow in an ultra-low temperature refrigerator. Wherein the curve h is a typical trend of the mass flow in the G-M refrigerator, the mass flow passing through the rotary valve 2b increases abruptly at the moment of opening the intake and exhaust, and the mass flow peak occurs at two places just after the intake process and just after the exhaust process; both peaks occur when the rotary valve 2b is open. By changing the shape of the rotary valve concave part 31 and the low-pressure gas outflow port 32, the invention can improve the mass flow passing through the rotary valve 2b, so as to make sinusoidal change i along with time, reduce irreversible loss and improve the efficiency of the ultralow temperature refrigerator.
The embodiments of the single-stage G-M refrigerator have been described above. The technical scheme of the invention is not limited to the above, and the air intake and exhaust structure according to the embodiment can be applied to ultralow temperature refrigerators such as a two-stage or multi-stage G-M refrigerator or pulse tube refrigerator.
The above embodiments are only for illustrating the technical idea of the present invention, and the protection scope of the present invention is not limited by the above embodiments, and any modification made on the basis of the technical scheme according to the technical idea of the present invention falls within the protection scope of the present invention; the technology not related to the invention can be realized by the prior art.
Claims (7)
1. Valve train, comprising a valve (2 a) provided with a high pressure gas inflow opening (20) and a valve orifice (21) and a rotary valve (2 b) provided with a rotary valve recess (31) and a low pressure gas outflow opening (32), characterized in that: the front section area of the rotary valve concave part (31) can be overlapped with the air distribution valve air hole (21) so that the rotary valve concave part (31) is in fluid connection with the air distribution valve air hole (21), and the section width of the front section area of the rotary valve concave part (31) gradually increases from the front end to the rear end of the rotary valve concave part (31); the whole area of the low-pressure gas outflow opening (32) can be overlapped with the distributing valve air hole (21) so that the low-pressure gas outflow opening (32) is in fluid connection with the distributing valve air hole (21), and the section width of the front section area of the low-pressure gas outflow opening (32) gradually increases from the front end to the rear end of the low-pressure gas outflow opening (32); the contour line of the front section area of the rotary valve concave part (31) is a curve; the contour line of the front section area of the low-pressure gas outflow port (32) is a curve; the outer edge contour line of the front section area of the rotary valve concave part (31) is internally tangent to the inner edge of the outer edge contour line of the air distributing valve air hole (21); the contour line of the rotary valve concave part (31) comprises a concave part semicircular arc (31 d) at the rear section, a concave part first straight line (31 c) and a concave part second straight line (31 e) at the middle section, a concave part first arc (31 a) and a concave part second arc (31 b) at the front section, a concave part semicircular arc (31 d), a concave part second straight line (31 e) at the outer side, a concave part first arc (31 a) at the outer side, a concave part second arc (31 b) at the inner side and a concave part first straight line (31 c) at the inner side, which are sequentially connected end to form the contour line of the rotary valve concave part (31).
2. A valve train according to claim 1, wherein: the middle section contour line and the rear section contour line of the low-pressure gas outflow opening (32) are overlapped with the corresponding contour lines of the distributing valve air holes (21).
3. A valve train according to any one of claims 1-2, wherein: the contour line of the low-pressure gas outflow port (32) comprises an outflow port semicircular arc (32 a) at the rear section, an outflow port inner circular arc (32 b) and an outflow port outer circular arc (32 d) at the middle section, an outflow port first circular arc (32 c) and an outflow port second circular arc (32 e) at the front section, an outflow port semicircular arc (32 a), an outflow port outer circular arc (32 d) at the outer side, an outflow port first circular arc (32 c) at the outer side, an outflow port second circular arc (32 e) at the inner side and an outflow port inner circular arc (32 b) at the inner side which are sequentially connected end to form the contour line of the low-pressure gas outflow port (32); the outflow inner circular arc line (32 b) and the outflow outer circular arc line (32 d) have the same central angle.
4. A valve train according to any one of claims 1-2, wherein: the air distribution valve air hole (21) is an annular elliptical groove, and the contour line of the air distribution valve air hole (21) is composed of an air hole first semicircular arc (21 a), an air hole outer circular arc (21 d), an air hole second semicircular arc (21 b) and an air hole inner circular arc (21 c) which are connected end to end in sequence.
5. A valve train according to claim 1, wherein: in a first phase of the rotation direction of the rotary valve (2 b), the rotary valve concave part (31) is connected with the air distributing valve air hole (21) at a first opening degree and gradually changes from the first opening degree to a second opening degree, and the first opening degree is smaller than the second opening degree; in a third phase of the rotation direction of the rotary valve (2 b), the rotary valve recess (31) is separated from the air distribution valve air hole (21).
6. A valve train according to claim 1, wherein: in a fourth phase of the rotation direction of the rotary valve (2 b), the low-pressure gas outflow opening (32) is in fluid connection with the distributing valve air hole (21) at a third opening, and gradually changes from the third opening to a fourth opening, wherein the third opening is smaller than the fourth opening; in a sixth phase in the rotation direction of the rotary valve, the low-pressure gas outlet (32) is separated from the gas distribution valve gas hole (21).
7. An ultra-low temperature refrigerator comprising a valve train according to any one of claims 1 to 6, and a compressor and an expander.
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| CN214841821U (en) * | 2021-05-08 | 2021-11-23 | 中船重工鹏力（南京）超低温技术有限公司 | Valve mechanism and ultralow temperature refrigerator comprising same |
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| KR101181003B1 (en) * | 2006-07-27 | 2012-09-07 | 한라공조주식회사 | The Sealing Assembly for Driving Shaft of Compressor |
| CN101852506A (en) * | 2010-05-14 | 2010-10-06 | 南京柯德超低温技术有限公司 | Implementation method of pulse tube refrigerator capable of being installed and used at any angle, and device thereof |
| CN102305499B (en) * | 2011-09-29 | 2013-11-06 | 南京柯德超低温技术有限公司 | Novel air distributing device for cryo refrigerator |
| JP6636356B2 (en) * | 2016-02-18 | 2020-01-29 | 住友重機械工業株式会社 | Cryogenic refrigerator |
| JP6771293B2 (en) * | 2016-03-16 | 2020-10-21 | 住友重機械工業株式会社 | GM freezer |
| JP6773872B2 (en) * | 2019-11-11 | 2020-10-21 | 住友重機械工業株式会社 | GM freezer |
| CN112325517B (en) * | 2020-11-09 | 2022-06-07 | 深圳供电局有限公司 | Valve mechanism and cryogenic refrigerator |
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| CN214841821U (en) * | 2021-05-08 | 2021-11-23 | 中船重工鹏力（南京）超低温技术有限公司 | Valve mechanism and ultralow temperature refrigerator comprising same |
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