RU2320941C1 - Cold production device - Google Patents

Abstract

FIELD: medicine, particularly refrigeration equipment for gas liquefaction.

SUBSTANCE: device comprises drive-activated compressor, outer heat-exchanging apparatus, manifold including pipelines and regenerator and connecting variable-volume cavity of compressor with variable-volume cavity of expander, as well as load heat-exchanger communicated with variable-volume cavity of expander. Phase of volume change in variable-volume expander cavity is shifted through predetermined angle with respect to that of variable-volume compressor cavity communicated therewith. Compressor and expander are made in accordance with rotor-blade scheme. Compressor and expander have output shafts connected to opposite end of outlet drive shaft by means of transmission mechanisms including round and non-round gear-wheels. Compressor, expander, transmission mechanisms and drive are axially aligned with each other. Each of compressor and expander include not less than one additional variable-volume cavity. Each additional variable-volume cavity of compressor is communicated with at least one variable-volume cavity of expander through additional line including pipelines and regenerator. Compressor body comprises outer heat-exchanging apparatus.

EFFECT: increased service life and reliability.

2 cl, 8 dwg

Description

The invention relates to refrigeration, and in particular to devices for producing cold, which are widely used, especially in cryogenic technology, and can be used in medicine, for liquefying gases and in other areas of technology that require reliable and efficient sources of cold, as well as when creating gas cryogenic machines according to the rotor-blade scheme.

A known piston system with reciprocating pistons (patent RU 2193089 C2, F01C 9/00, F04C 9/00, F02B 53/00), including a cylinder having an annular and hollow inner space, many pistons from which are formed the first and second groups to be alternately placed on the same inner circumference of the cylinder, while the first and second groups of pistons make a reciprocating movement along a given arc with the same speed and in opposite directions with respect to each other, many the number of inlet valves installed at each point of the cylinder, where two adjacent pistons meet, and designed to control the flow of fluid introduced into them from the outside, and the set of exhaust valves installed at each point of the cylinder where two adjacent pistons meet, and designed to regulate fluid flow displaced from the inside out.

The disadvantages of this system are the design complexity, the presence of intake and exhaust valves, creating additional dead volume and limiting the resource and reliability of the device. In addition, such a system requires a bulky drive with a crank mechanism, creating a high level of vibration.

Known cryogenic gas machine (patent RU 2013717 C1, F25B 9/00), containing a cylinder, a hollow displacement piston installed in it using elastic elements, dividing the internal volume of the cylinder into two cavities - warm and cold, interconnected through series-connected regenerator and load heat exchanger, and a compression unit connected to a warm cavity, an inertial element inside a hollow displacement piston connected through an elastic element to the end surface of the piston.

Known cryogenic gas machine type PP (V.N. Novotelnov and others. Cryogenic machines, St. Petersburg: "Polytechnic", 1991, p.192), consisting of two piston assemblies. One of them performs the function of a compressor and includes a cylinder, a piston, an external heat exchange apparatus (ABT) for heat removal to the environment, and a part of the regenerator. Another node performs the function of an expander and includes a cylinder, piston, AWT for supplying heat to the cycle (load heat exchanger) for the cooled device, part of the regenerator.

The disadvantages of the known and also the above-described machines are a high level of vibration, piston wear on the cylinder wall, which leads to the flow of the working fluid through the gaps of the annular cavity between the piston and the cylinder, clogging of the working fluid by wear products and reduces the life and reliability of these machines.

The aim of the invention is to increase the resource and reliability of the device for producing cold.

This goal is achieved by the fact that in the device for producing cold, containing a compressor driven by a drive, an external heat exchange apparatus (ABT), a line containing pipelines and a regenerator and connecting a cavity of variable volume of the compressor with a cavity of variable volume of the expander, a heat exchanger connected to the cavity of the variable volume of the expander, and in the cavity of the variable volume of the expander the phase of the change of the variable volume is shifted by a predetermined angle relative to the phase of the change of the variable volume the compressor cavity that is integrated with it, the compressor and the expander are made according to the rotor-blade scheme, the input shafts of which are connected to the opposite ends of the drive output shaft by means of gears with round and non-circular gears, the compressor, expander, gears, the drive placed on one axis, the compressor and the expander contain at least one additional cavity of variable volume each, each additional cavity of variable volume of the compressor is connected by an additional line, containing aschey regenerator and piping, at least one cavity with variable volume expander, at least one of the cavities of variable volume expander connected to a load heat exchanger, AVT placed on the compressor casing.

The invention is illustrated graphically on the example of a device for producing cold (UPH) of a rotor-blade scheme.

Figure 1 shows the UPH, a longitudinal vertical section of the main view.

Figure 2 shows the compressor, the transmission gear of the compressor and the drive UPH.

Figure 3 shows the expander and the transmission mechanism of the expander.

Figure 4 shows the kinematic diagram of the UPH.

Figure 5 shows the operation of the UPH (phase 1).

Figure 6 shows the operation diagram of the UPX device (phase 2).

Figure 7 shows the operation of the UPH (phase 3).

On Fig shows a diagram of the UPH (phase 4).

A device for producing cold contains a compressor 1 and expander 2 (Figure 1), made according to a rotor-blade scheme, two lines 3 and 4 (Figure 5), connecting pairs of diametrically opposite cavities of variable volume (PPO) 5, 6 and 7 , 8 (Figs. 5-8) of compressor 1 (Fig. 1) with corresponding diametrically opposite pairs of PPO 9, 10 and 11, 12 (Figs. 5-8) of expander 2 (Fig. 1), the transmission gear of the compressor (PMC ) 13 (FIG. 1) and the expander’s transmission mechanism (PMD) 14 (FIG. 1), drive 15 (for example, an electric motor) (FIG. 1). PMK 13 (Fig. 1) contains a pinion shaft 16 (Figs. 1, 2, 4) mounted on the output shaft 17 (Figs. 1, 2) of the drive 15 (Fig. 1) from the compressor 1 (Fig. 1) , carrier 18 (Fig. 2, 4), housing 19 (Fig. 2), non-circular gear wheel 20 (Figs. 1, 2, 4) PMK 13 (Fig. 1), rigidly mounted on an external input shaft 21 (Fig. 2) compressor 1 (Fig. 1), a non-circular gear wheel 22 (Figs. 1, 4) PMK 13 (Fig. 1), rigidly mounted on the internal input shaft 23 (Figs. 1, 2) of compressor 1 (Fig. 1) .

In the carrier 18 (FIGS. 2, 4), from the drive 15 side, two round gears are mounted diametrically opposite - the satellites 24 (FIGS. 2, 4) and 25 (FIG. 2) with the possibility of rotation around their axes, and from the compressor side 1 (Fig. 1) two blocks of gears 26 (Figs. 1, 4) and 27 (Fig. 1) are mounted diametrically opposed with rotation around their axes.

In the housing 19, a central stationary gear wheel with internal gearing 28 (FIGS. 2, 4) and a fixed central circular gear wheel with external gearing 29 (FIGS. 2, 4) are installed.

Satellites 24 (FIG. 2) and 25 (FIGS. 2, 4) are interfaced with a central fixed gear with internal gear 28 (FIGS. 2, 4).

The block of gears 26 (Fig. 1, 4) contains a round gear wheel 30 (Fig. 1, 4) mounted on the compressor side 1 (Fig. 1), a non-circular gear wheel 31 (Figs. 1, 4), a non-circular gear wheel 32 (Fig.1, 4), fixed relative to each other in axial and angular position, and the angle between the major semi-axes of the non-circular gears 31 (Figs. 1, 4) and 32 (Figs. 1, 4) is 90 °.

The block of gears 27 (Fig. 1) contains a round gear 33 (Fig. 1) mounted on the compressor side 1 (Fig. 1), a non-circular gear 34 (Fig. 1), a non-circular gear 35 (Fig. 1), fixed relative to each other in axial and angular position, and the angle between the large semi-axes of the non-circular gears 34 and 35 is 90 °. The round gears 30 (Figs. 1, 4) and 33 (Fig. 1) of the gear blocks 26 (Figs. 1, 4) and 27 (Fig. 1) are mated to the stationary central round gear with external gearing 29 (Fig. 2) , four).

Compressor 1 (FIG. 1) contains a housing 36 (FIG. 2), an external input shaft 21 (FIG. 2) with two blades 37 and 38 mounted on one end in the cavity of compressor 1 (FIG. 1) (FIG. 1, 4) in diametrically opposite directions, a non-circular gear wheel 20 is installed on its other end (Figs. 1, 4), coaxial with the external input shaft 21 (Fig. 2), the internal input shaft 23 (Fig. 1) with one mounted on it the end in the cavity of the compressor 1 (Fig. 1) with two blades 39 and 40 (Figs. 1, 4) in the diametrically opposite direction, at its other end there is a non-circular gear tooth EDC 22 (1, 4), an external heat exchange unit (VDU) 41 (2) (e.g., refrigerator) connected to the compressor body 1 (Figure 1).

Non-circular gears 31 and 34 (Fig. 1) in gear blocks 26 and 27 (Fig. 1) PMK 13 (Fig. 1) are coupled with a non-circular gears 20 (Figs. 1, 4) of an external input shaft 21 (Fig. 2) ) compressor 1 (Fig. 1), and non-circular gears 32 and 35 (Fig. 1) in gear blocks 26 (Figs. 1, 4) and 27 (Fig. 1) PMK 13 (Fig. 1) are paired with a non-circular gear the wheel 22 (Fig.1, 4) on the inner input shaft 23 (Fig.1) of the compressor 1 (Fig.1).

In line 3 (Figure 5), the collector 42 (Figure 1, 6) connects diametrically opposed software 5 and 6 (Figure 5) of the compressor 1 (Figure 1) through a pipe 43 (Figure 1, 6) with the regenerator 44 (Fig. 1, 6). The regenerator 44 (Fig. 1, 6) is connected through a pipe 45 (Fig. 1, 6) and a collector 46 (Fig. 6) with diametrically opposed PPO 9 and 10 (Fig. 5-8) of the expander 2 (Fig. 1) . In line 4 (FIG. 5), a collector 47 (FIG. 6) connects diametrically opposed PPOs 7 and 8 (FIGS. 5-8) of compressor 1 (FIG. 1) through a conduit 48 (FIG. 6) to a regenerator 49 (FIG. .6). The regenerator 49 (Fig.6) is connected through a pipe 50 (Fig.6) and a collector 51 (Fig.6) with diametrically opposed PPO 11 and 12 (Fig.5-8) of the expander 2 (Fig.1).

PMD 14 (Fig. 1) contains a pinion shaft 52 (Figs. 1, 4) mounted on the output shaft 17 (Fig. 1) of the drive 15 (Figs. 1, 4) from the expander 2 (Fig. 1), carrier 53 (Fig. 1, 4), housing 54 (Fig. 3), a non-circular gear wheel 55 (Fig. 1, 4), rigidly mounted on an external output shaft 56 (Fig. 1) PMD 14 (Fig. 1), non-circular gear wheel 57 (Fig. 1, 4) PMK 14 (Fig. 1), rigidly mounted on the internal output shaft 58 (Fig. 1) of the PMC 14 (Fig. 1).

In the carrier 53 (Figs. 1, 4), from the drive 15 side, two round gears are mounted diametrically opposite - the satellites 59 (Fig. 3) and 60 (Fig. 4) with the possibility of rotation around their axes, and from the expander 1 ( Figure 1) two blocks of gears 61 (Figs. 1, 4) and 62 (Fig. 1) are mounted diametrically opposed with rotation around their axes.

In the housing 54 (FIG. 3), a central fixed gear with internal gearing 63 (FIGS. 1, 4) and a fixed central circular gear with an external gearing 64 (FIGS. 1, 4) are installed.

Satellites 59 (FIG. 3) and 60 (FIG. 4) are associated with a central fixed gear with internal gearing 63 (FIGS. 1, 4).

The gear block 61 (Fig. 1, 3) contains a circular gear wheel 65 (Fig. 1) mounted on the side of the expander 1 (Fig. 1), a non-circular gear wheel 66 (Fig. 1), a non-circular gear wheel 67 (Fig. 1) ), fixed relative to each other in axial and angular position, and the angle between the large semi-axes of the non-circular gears 66 (Figure 1) and 67 (Figure 1) is 90 °.

The gear block 62 (Fig. 3, 4) contains a non-circular gear wheel 68 (Fig. 1, 4) mounted on the side of the expander 2 (Fig. 1), a circular gear wheel 69 (Figs. 1, 4), a non-circular gear wheel 70 (Fig.1, 4), fixed relative to each other in axial and angular position, and the angle between the major semi-axes of the non-circular gears 69 (Figs. 1, 4) and 70 (Figs. 1, 4) is 90 °.

Round gears 65 and 68 (Fig. 1) of gear blocks 61 (Figs. 1, 3) and 62 (Figs. 1, 4) are mated to a stationary central round gear with external gear 64 (Figs. 1, 4).

Non-circular gears 66 (Fig. 1) and 69 (Figs. 1, 4) in gear blocks 61 (Figs. 1, 3) and 62 (Figs. 3, 4) are mated to a non-circular gears 55 (Figs. 1, 4 ) rigidly mounted on the external output shaft 56 (Fig. 1) PMD 14 (Fig. 1), and non-circular gears 67 (Fig. 1) and 70 (Figs. 1, 4) in gear blocks 61 (Fig. 1, 3) and 62 (Figs. 3, 4) are interfaced with a non-circular gear wheel 57 (Fig. 1) rigidly mounted on the internal output shaft 58 (Fig. 1) of the PMD 14 (Fig. 1). The external output shaft 56 (FIG. 1) of the PMD 14 (FIG. 1) is connected to the external input shaft 71 (FIG. 3) of the expander 2 (FIG. 1), and the internal output shaft 58 (FIG. 1) of the PMD 14 (FIG. 1) is connected to the internal input shaft 72 (Figure 3) of the expander 2 (Figure 1).

The expander 2 (Fig. 1) contains a housing 73 (Fig. 3), an external input shaft 71 (Fig. 3) with two blades 74 (Figs. 1, 4) mounted on one end thereof in the cavity of the expander 2 (Fig. 1) and 75 (Figs. 1, 4) in a diametrically opposite direction, and connected at the other end to an external output shaft 56 (Fig. 1) PMD 14 (Fig. 1), coaxial with an external input shaft 71 (Fig. 3), an internal input shaft 72 (Fig. 3) with two blades 76 (Figs. 1, 4) and 77 (Figs. 1, 4) mounted at one end in the cavity of the expander 2 (Fig. 1) and diametrically opposed, and connected by another end with inner in output shaft 58 (Figure 1) PMD 14 (Figure 1). The housing 54 (Figure 3) is connected through a casing 79 (Figure 3) and a heat insulator 80 (Figure 3) with the front cover 81 (Figure 3) of the expander 2 (Figure 1), the housing 73 (Figure 3) and the back cover 82 (FIG. 3) of the expander 2 (FIG. 1).

The front cover 81 (FIG. 3) of the expander 2 (FIG. 1) is connected through a jacket 83 (FIG. 3) to the housing 54 (FIG. 3).

The back cover 82 (Figure 3) of the expander 2 (Figure 1) acts as a load heat exchanger.

Compressor 1, expander 2, PMK 13 and PMK 14, drive 15 (Figure 1) are placed on the same axis.

A device for producing cold works as follows.

The workflow in UPH can be conditionally divided into 4 phases, smoothly transitioning from one to another.

I phase. Compression of the working fluid-gas (RTG). In this phase, in the PPO 5 and 6 (Figure 5), the volume changes from the maximum to an intermediate value with an increase in the pressure and temperature of the RTG in the closed volume formed by the PPO 5 and 6 (Figure 5) by the internal cavities of the line 3 (Figure 5) and PPO 9 and 10 (Figure 5). In this case, in the software 9 and 10 (Figure 5) in this phase, the volume changes from intermediate to minimum with the displacement of the RTG from the software 9 and 10 (Figure 5) to the highway 3 (Figure 5) connected to the software 5 and 6 (FIG. 5). During this period, the compression heat of the RTG is removed from the housing 36 (Figure 2) of the compressor 1 (Figure 1) in the AWT 41 (Figure 2) to reduce the temperature of the RTG compressible in the software 5 and 6 (Figure 5), which changes the temperature from intermediate to maximum. Next, there is a decrease in the temperature of the RTG due to heat removal from it in the regenerator 44 (Fig.1, 6).

II phase. Extrusion of RTG. In this phase, in the software 5 and 6 (Fig. 6), the volume changes from intermediate to the minimum value with the displacement of the RTG from the software 5 and 6 (Figure 6) to the highway 3 (Figure 3) connected to the software 9 and 10 ( 5). In this case, in the software 5 and 6 (Fig.6) in this phase, the volume changes from the minimum to the intermediate value with the work to overcome the friction forces.

III phase. Expansion of RTG. During this phase, in the software 5 and 6 (Fig.7) there is a change in volume from a minimum to an intermediate value. In this case, in the software 9 and 10 (Fig.7) in this phase, the volume changes from intermediate to maximum value with the work to overcome the friction forces. In PPO 9 and 10 (Fig. 7), the RTG expands with cooling to a predetermined temperature of the back cover 81 (Fig. 3) of the expander 2 (Fig. 1), which acts as a load heat exchanger.

IV phase. Reverse crowding out of expanded RTG. In this period, in the software 5 and 6 (Fig. 8), the volume changes from intermediate to maximum, and in the software 9 and 10 (Fig. 8), the volume changes from the maximum to intermediate with the displacement of the cooled RTG to line 3 (Fig. .5). In the regenerator 44 (FIGS. 1, 6), the RTG is heated with simultaneous cooling of the regenerator 44 (FIGS. 1, 6). At the inlet to the compressor 1 (Figure 1), the temperature of the RTG in steady state corresponds to the temperature of the RTG upon exiting the compressor in phases I and II.

The processes taking place in the software 7 and 8 (Figure 5-8) of the compressor 1 (Figure 1), the highway 4 (Figure 5) connecting the software 7 and 8 (Figure 5-8) of the compressor 1 (Figure 1) with PPO 11 and 12 (Figure 5-8) of expander 2 (Figure 1), in PPO 11 and 12 (Figure 5-8) of expander 2 (Figure 1) are similar to the above processes and proceed in antiphase relative to the corresponding processes in PPO 5 and 6 (Figs. 5-8) of compressor 1 (Fig. 1), line 3 (Fig. 5) connecting PPO 5 and 6 (Figs. 5-8) of the compressor with PPO 9 and 10 (Figs. 5- 8) expander, in PPO 9 and 10 (Fig.5-8). In this case, the phase of change of each variable volume in the compressor 1 (Figure 1) is shifted by 90 ° relative to the phase of change of the variable volume of the expander 2 connected to it (Figure 1).

It should be noted that in all phases the period occurs in the AWT 41 (Figure 2) the compression heat of the RTG from the housing 36 (Figure 2) of the compressor 1 (Figure 1), as well as the removal of heat fluxes from the heat exchanger load to reduce the temperature of the RTG, compressible in the compressor 1 (Figure 1).

The indicated phases of the working process are repeated cyclically during the operation of the UPH.

This is the totality of essential features that provides a technical result in all cases to which the requested amount of legal protection applies. The applicant has not identified sources containing information about technical solutions identical to the present invention, which allows us to conclude that it meets the criterion of "novelty."

The proposed technical solution improves the reliability of the device by reducing vibrations, reducing the flow of the working fluid through the gaps of the annular cavity between the blades and the compressor and expander bodies, reducing the wear of contacted surfaces in the PPO and, as a result, reducing the clogging of the working fluid by wear products.

Claims (1)

A device for producing a cold, comprising a compressor driven by a drive, an external heat exchange apparatus (ABT), a line containing pipelines and a regenerator and connecting a cavity of variable volume of the compressor with a cavity of variable volume of the expander, a heat exchanger connected to the cavity of variable volume of the expander, the cavity of the variable volume of the expander, the phase of the change of the variable volume is shifted by a predetermined angle relative to the phase of the change of the variable volume of the compressor cavity connected to it, characterized in that the compressor and the expander are made according to the rotor-blade scheme, the input shafts of which are connected to the opposite ends of the drive output shaft by means of gears with round and non-circular gears, the compressor, expander, gears, the drive are located on the same axis, the compressor and expander at least one additional cavity of variable volume each, each additional cavity of variable volume of the compressor is connected by an additional line containing pipelines and reg generator, with at least one cavity of variable volume of the expander, at least one of the cavities of variable volume of the expander is connected to the load heat exchanger, the AVT is placed on the compressor casing.

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