RU2230224C1 - Heat compressor - Google Patents

Abstract

FIELD: applicable in various branches of equipment for compression and transfer of gas. SUBSTANCE: the compressor has a cylinder, ejector pump with a built-in generator and radially inclined holes for connection of the regenerator to the cylinder cold a hot spaces, respectively. The ejector pump is actuated by an electric drive with a rotor located on the outer side of the ejector pump, and a stator located on the cylinder. The cylinder has an extended surface heat exchanger, heat exchanger of heat-transfer agent with a heat insulation, and a refrigerant heat exchanger, gas main with inlet and discharge valves. The ejector pump has end-piece blanks. On the side of the cold space the blank has a ring-shaped end-face axial groove with a rectangularestion spring installed in it. On the one side the spring is fastened on the cylinder end face in its cold space, and on the other side-on the bottom of the ring-shaped end-face axial groove so that the spring can operate in compression-tension. EFFECT: enhanced reliability, simplified construction. 1 dwg

Description

The invention relates to compressor engineering, namely to heat-using compressors, and can be used in various fields of technology for compression (compression) and injection of gases.

Known compressor [1] - / USSR Copyright Certificate No. 1605110, class. F 25 B 9/00, 1990 /, containing a displacer installed in the cylinder cavity with axial movement, with a regenerator and inclined channels located in it, dividing the cylinder cavity into warm and cold cavities, heat and coolant heat exchangers located at the ends of the cylinder , an electric drive, the stator of which is located on the outer side of the cylindrical body, and the rotor is on the displacer body, as well as intake and exhaust valves.

The disadvantages of the known analogue are:

- insufficient heat exchange surface of the end and side walls of the cylindrical body to transfer the required amount of heat, which leads to an increase in the temperature difference between, respectively, the coolant and the working fluid in the hot cavity and the refrigerant (medium for heat removal) and the working fluid in the cold cavity, and this , in turn, leads to greater irreversibility of heat transfer processes and lower efficiency;

- the presence of a large dead volume due to the need to prevent displacer blows on the end walls of the cylindrical body, which can lead to compressor failure;

- a large mass of the displacer with a built-in regenerator and rotor of the electric motor will lead to large inertial forces (at medium and high frequencies), to compensate for which it will be necessary to significantly increase the power, and therefore the mass of the linear motor, which will lead to a relatively large expenditure of electric energy for the drive displacer, and this is completely undesirable for any device;

- low reliability and resource of the thermal compressor due to the placement of valves in its working cavity, especially in the warm zone;

- cold gas entering the warm zone must be pre-cooled, and this is an additional energy expenditure;

- for normal operation of the regenerator, it is required to maintain the set temperature values at its ends, and this condition is poorly ensured as a result of different gas paths (along the gap and the central channel and the organization of the input and output of compressed gas from different ends of the cylinder), which reduces the efficiency of the regenerator and the heat compressor as a whole.

The prototype of the proposed device is a thermal compressor [2] - / Patent of Russia No. 2183767, class. F 04 V 19/24, F 25 V 9/00, publ. 06/20/2002, bull. No. 17 /, comprising a displacer installed in the cylinder cavity with the possibility of axial movement, with channels and a regenerator dividing the cylinder cavity into cold and hot cavities, a heat insulated heat exchanger and a refrigerant heat exchanger located at the cylinder ends, inlet and outlet valves located on the external line connected through the heat exchanger of the refrigerant to the cold cavity of the cylinder at its end, an electric drive biased towards the cold cavity, the stator of which is located on the external the cylinder side, and the rotor on the displacer body, a finned heat exchanger located on the outer side of the cylinder between the stator and the heat carrier, the displacer is closed by end profile plugs, in which ring-shaped end axial recesses have rectangular springs, with which the displacer is spring-loaded from the end internal walls of the cylinder the inner side sections of which and the side side external areas of the displacer contain threads (fins) with the formation of gaps (thread in the gap rah made to improve the heat transfer coefficient).

The disadvantage of the prototype is that the compression spring located in the hot cavity operates in extreme (extreme) conditions and has low reliability, which reduces the reliability of the entire thermal compressor.

This drawback sets the task of increasing the reliability of the heat-using compressor and simplifying its design.

This task is achieved by the fact that in a thermal compressor containing a spring-loaded displacer installed in the cylinder cavity with the possibility of axial movement, with channels and a regenerator separating the cylinder cavity into cold and hot cavities, a heat-insulated coolant heat exchanger and a refrigerant heat exchanger located at the ends of the cylinder, inlet and exhaust valves located on an external line connected through a refrigerant heat exchanger to the cold cavity of the cylinder at its end, the actuator is biased located in the direction of the cold cavity, the stator of which is located on the outer side of the cylinder, and the rotor is on the displacer body, a finned heat exchanger located on the outer side of the cylinder between the stator and the heat transfer agent heat exchanger is closed by end profile plugs, in which ring-shaped axial end recesses are installed sections, internal frontal sections of the cylinder and external frontal sections of the displacer contain threads (fins), with the formation of gaps, in the hot cavity rtsevaya plug is flat (and installed without the spring), but in the cold cavity spring fastened to operate in a compression mode - stretching.

Fastening in the cold cavity of the spring with the possibility of working in compression - stretching mode is necessary to exclude the spring from the hot cavity and to ensure the displacer self-oscillating motion. In this case, the spring should be compared with the spring of the prototype twice as high stiffness for the perception of double load with the same parameters of the displacer.

Performing a flat end cap in the hot cavity is necessary because of the unnecessary profile axial ring-shaped undercut.

The implementation of the thermal compressor in combination with the above features (features of the claims) is new to thermal compressors and, therefore, meets the criterion of “novelty”.

The above set of distinctive features is not known at this level of technology and does not follow from the well-known rules for the design of thermal compressors and their auxiliary equipment, which proves compliance with the criterion of "inventive step".

The constructive implementation of a thermal compressor with the indicated set of essential features does not present any structural, technical and technological difficulties, from which the criterion “industrial applicability” follows.

The drawing schematically shows the design of a thermal compressor.

The thermal compressor comprises a cylinder 1, a displacer 2 with a regenerator 3 and radially inclined holes 4 and 5, respectively directed to the sides of the cold cavity 6 and hot cavity 7, for the working fluid, which is the pumped gas. The displacer 2 on its outer side has an electric drive rotor 8 installed in it, the stator 9 of which is located on the outer surface of the cylinder 1. The cylinder 1 is equipped on the side of the hot cavity 7 with a heat exchanger 11, which is insulated from the environment by a layer of thermal insulation 12, and on the cold side cavity 6 with a heat exchanger of refrigerant 10, through which a gas line 13 is suitable, with inlet 14 and outlet 15 valves for pumped gas installed on it. The displacer 2 from the cold 6 and warm 7 cavities of the cylinder 1 has end caps, respectively. From the side of the cold cavity in the plug, an annular end axial undercut 16 is made with a spring 17 of rectangular cross section installed therein. The spring 17 is fixed on one side at the end of the cylinder 1 in its cold cavity, and on the other hand, at the bottom of the annular end axial undercut 16, so that the spring 17 can operate in compression-tension mode. Threaded sections 18 are located on the external front-end sections of the displacer 2, made with a smaller radius than its middle part, and on the inner surface of the front-end sections of the cylinder 1, there are threaded sections 19 with the formation of annular gaps 20 located in the cold 6 and hot 7 cavities of the cylinder 1. On the outer side of the cylinder 1 between the heat insulation 12 of the heat exchanger-heat carrier 11 and the stator 9 of the electric drive there is a finned radiator (heat exchanger) 21.

The proposed thermal compressor operates as follows.

In the steady state, the displacer 2 moves reciprocating along the cylinder 1 under the action of the spring 17 installed in the recess 16 and performs a self-oscillating movement supported by an electric drive consisting of a stator 9 and rotor 8. In this case, the power of the linear motor is spent only on maintaining the self-oscillating reciprocating - translational movement of the displacer, that is, to overcome the friction forces and hydraulic resistance. When the displacer 2 moves toward the warm cavity 7, the hot gas passes through the gap 20 (hot cavity), the holes 5, the regenerator 3, cooling it and, passing through the holes 4 and the gap 20 (cold cavity), additionally cooling, passing through the holes 4 enters the cavity 6. As the gas cools, the pressure in the entire volume of the housing 1 drops and becomes smaller than at the inlet to the compressor, as a result of which the inlet valve 14 opens, and the next portion of gas for compression enters the compressor. When the displacer 2 moves towards the cold cavity 6, cold gas passes through the gap 20 (cold cavity), the holes 4, the regenerator 3, heats up in it, and passing through the holes 5 and the gap 20 (hot cavity), additionally being heated, gets into the hot cavity 7. As the gas heats up, the pressure in the entire volume of cylinder 1 grows and becomes larger than at the inlet to the compressor, as a result of which the exhaust valve 15 opens, and the next portion of compressed gas comes from the heat compressor to the consumer. After the start of the movement of the displacer 2 towards the cold cavity 6, the entire cycle is repeated. The finned heat exchanger 21 prevents the starter 9 from being overheated by the heat of the coolant supplied by the heat conduction from the heat exchanger along the wall of the housing 1.

The present invention solves the problem of improving the reliability of a thermal compressor, since the compression spring originally operating in a hot cavity, operating in extreme (extreme) conditions and having low reliability, has been removed from its design. Fixed with the ability to work in compression mode - stretching in a cold cavity, the spring provides a displacer self-oscillating motion. The spring should be twice as hard as the prototype spring to absorb double load with the same parameters of the displacer.

Sources of information

1. USSR Copyright Certificate No. 1605110, class F 25 B 9/00, 1990

2. Patent of Russia No. 2183767, cl. F 04 V 19/24, F 25 V 9/00, publ. 06/20/2002, bull. No. 17 is a prototype.

Claims (1)

A heat compressor comprising a spring-loaded displacer installed in the cylinder cavity with axial movement and canals and a regenerator separating the cylinder cavity into cold and hot cavities, a heat insulated heat exchanger and a refrigerant heat exchanger located at the cylinder ends, an inlet and outlet valve located on the external line, connected through the heat exchanger of the refrigerant to the cold cavity of the cylinder at its end, the actuator is biased towards the cold cavity, stat which is located on the outer side of the cylinder, and the rotor is on the displacer body, a finned heat exchanger located on the outer side of the cylinder between the stator and the heat carrier, the displacer is closed by end caps, in which ring-shaped end axial recesses have rectangular springs, inner end sections of the cylinder and the front-end external sections of the displacer contain threads (fins) with the formation of gaps, characterized in that in the hot cavity the end cap is made flat (without springs installed), and the cold cavity spring fastened to operate in a compression mode - stretching.