Heating steam circulation driving device in parallel heating system

Abstract

The invention relates to the field of tire vulcanization technology and equipment in tire production and manufacturing, in particular to a heating steam circulation driving device in a parallel heating system, which is used in an external temperature parallel heating system of a double-mold vulcanizing machine and is used for providing a stable heating steam source for the parallel heating device. According to the invention, baffle plate shunting, small-caliber closure, jet driving and steam kinetic energy buffering technologies are adopted for treatment, so that the vulcanization external temperature heating steam enters the heating cavity and is changed into approximately static stable pressure supply from original large-impulse instant inrush; the influence of vortex, steam inlet angle and other factors in a heating pipe cavity on flow distribution is avoided, the steam inlet heating process of vulcanizing external temperature steam is more stable, heating devices connected in parallel are heated more evenly, meanwhile, through steam jet driving, vulcanizing external temperature tail steam is recycled, and the service life of the vulcanizing external temperature tail steam is prolonged. The influence of local high temperature of the tire blank on the quality due to excessive steam admission during temperature rise can be avoided, meanwhile, the loss of steam can be effectively reduced, and the purposes of saving energy and reducing cost are achieved.

Description

Technical Field

[0001] The invention relates to the field of tire vulcanization technology and equipment in tire production, and in particular to a heating steam circulation driving device in a parallel heating system. Technical Background

[0002] Vulcanization is one of the most critical processes in the tire production process. It is a process that heats and pressurizes the tire embryo to undergo chemical and physical reactions and finally shapes it into a finished tire. The steam consumption in this process accounts for 90%-98% of the total steam consumption, especially the consumption of steam for heating at external vulcanization temperature, which accounts for more than 60% of the total steam consumption and is one of the main energy consumption costs in tire production.

[0003] The external temperature of vulcanization refers to the heating temperature of the outside of the tire blank. It is usually heated by steam heating the upper hot plate, lower hot plate, mold sleeve and other heating devices, and then heating the tire blank by heat conduction. The upper and lower hot plates and mold sleeves and other devices used to provide the external temperature of vulcanization are collectively referred to as heating devices. The parallel heating system refers to the use of a set of steam inlet valves to provide heat sources for two heating devices at the same time through parallel pipelines, and run a set of PID algorithm controlled heating systems, such as parallel steam inlet heating of the left and right hot plates in a dual-mode vulcanizer, and parallel steam inlet heating of the left and right steamers.

[0004] The main steam supply of the vulcanization external temperature heating system is high-temperature saturated steam, with a pressure of more than 8kgf / cm^2 and a temperature of more than 175℃. The heating system adjusts the high-temperature saturated steam to the appropriate temperature for heating steam use according to different production process requirements. Taking the production of all-steel tires as an example, the required value of the external temperature is about 150℃, so the temperature of the heating steam is controlled at about 150℃.

[0005] The parallel heating control process is: take the measured temperature of one of the two parallel heating cavities as the main control feedback value. When the actual measured temperature is lower than the process set value, the PID operation result is greater than zero, the diaphragm regulating valve opens, and steam enters the external temperature heating cavity for heating until the measured tail steam temperature at the end of the heating device reaches the process set value, the PID output is zero, and the diaphragm regulating valve is closed, waiting for the steam in the external temperature heating cavity and the terminal pipeline to be cooled through natural heat consumption and discharge through the external drain valve until the measured temperature is lower than the process set value and the heating is started again. The entire vulcanization external temperature steam heating control process is repeated as described above.

[0006] Problems:

[0007] During heating, the opening degree of the steam inlet control valve is not synchronized with the actual temperature change, and the tire embryo is heated unevenly, which has a great impact on the quality of the tire:

[0008] The vulcanization external temperature control PID calculates the measured temperature and the set value, and drives the action of the diaphragm regulating valve with the calculation result. However, the PID calculation is an iterative algorithm with a very short sampling period. The temperature measurement has the characteristics of physical inertia and the time difference of temperature conduction of steam in the mold cavity. As a result, the execution action of the diaphragm regulating valve is seriously out of sync with the actual temperature change. That is, when the temperature measured by the sensor has not changed to the real temperature, the PID iterative calculation has already controlled the regulating valve to open at 100%, causing a large amount of heating steam to instantly flow into the external temperature heating chamber, causing the actual temperature in the heating chamber to be high at first and low at the end, resulting in uneven heating of the tire embryo.

[0009] The steam flow rates of the two branches in parallel are different, resulting in different heating temperatures of the parallel mold cavities:

[0010] When the diaphragm regulating valve is opened, a large amount of steam will instantly flow into the heating tube cavity, but the installation angles and welding roughness of the two parallel branch pipes are not exactly the same. Therefore, the rapidly pouring steam enters the two parallel branches at different angles and generates different eddies, which seriously affects the distribution of steam flow in the two parallel branches. This situation is an important factor in producing different heating effects of the two heating devices. The parallel heating system only uses the measured temperature of one side of the branch as the control temperature. The temperature on the other side is not easy to meet the process requirements of vulcanization, and there are serious quality risks.

[0011] Excessive consumption of heating steam results in high production energy costs:

[0012] The measuring points of the external temperature of the vulcanization are installed on the terminal tail steam pipeline of the external temperature vulcanization heating device, and the measured tail steam temperature is used as the control target temperature. Therefore, the temperature value of the sulfurization tail steam of the external temperature vulcanization heating device is in line with or slightly lower than the process standard value, contains great thermal value, and direct discharge causes great steam energy loss. Summary of the invention

[0013] In order to effectively solve the above problems, the present invention adopts small-caliber jets and steam kinetic energy buffering technology to control the steam intake of the left and right heating devices of the parallel heating system, so that the heating steam changes from the original large amount of instantaneous influx to approximately static stable pressure steam supply heating, avoiding the influence of factors such as steam intake angle and steam vortex on the steam intake flow and heating conditions of the parallel heating device. The principle is that the left and right heating devices of the parallel heating system control the entry of steam in the form of small-caliber jets respectively, and the high-speed steam flow formed by the jet draws the sulfurized tail steam and drives the circulating flow of the heating steam, and the kinetic energy of the steam is buffered by a kinetic energy buffer device before the high-speed jet steam enters the heating chamber, so that the high-speed jet steam is converted into smoothly flowing heating steam to provide a heat source for the heating device. The present invention adopts two groups of jets and steam buffer devices, one group is used to drive the circulating flow of steam in the two parallel heating devices respectively, and appropriately supplement the loss of steam in the cycle, and the other group is used to supplement more steam heat when heating is required.

[0014] The technical solution adopted by the present invention to solve the technical problem is as follows: two groups of jet devices with different spray paths are designed, each group of jet devices contains two identical jet heads, each jet head corresponds to a heating cavity in the parallel heating system, the two jet heads are wrapped by a collecting box, a circulating steam inlet is opened on the side of the collecting box, the collecting box stores the circulating steam that needs to be pulled, a buffer box for steam kinetic energy buffering is provided under each jet head, a steam discharge port is provided on the side of the buffer box, one group of jet devices is used to drive the steam circulation in the left and right heating cavities of the parallel heating system, and the other group is used to supplement more steam heat when the heating cavity is heated. A group of jet devices used to drive the steam circulation is called a circulation driver, and a group of jet devices used to supplement heat is called a temperature compensator. The circulation driver and the temperature compensator have similar composition structures, both of which are composed of two jet nozzles, two collecting boxes, and two buffer boxes as main components. In order to reduce the pipeline laying of the parallel heating system, two collectors used to connect the vulcanization tail steam pipeline as the circulating steam inlet can be combined into a common collector. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 : A three-dimensional schematic diagram of the device of the present invention.

[0016] Figure 2 : Three views of the device of the present invention.

[0017] Figure 3 : Planing view and partial enlarged view of the driver in the present invention.

[0018] Figure 4 : Planing view of the temperature compensator in the device of the present invention.

[0019] Figure 5 : Thermal piping diagram of parallel heating system.

[0020] Figure 6 : Streamline and cross-sectional diagrams of steam pressure and velocity when only the circulation drive is running in CFD simulation.

[0021] Figure 7 : Streamline diagram and cross-sectional diagram of steam pressure and velocity when CFD simulation cycle drive and compensator are running simultaneously.

[0022] Figure 1 Middle: S1. Circulation drive, S2. Make-up heater, 1. Driver high-pressure steam interface, 2. Tail steam collecting box, 3. Tail steam interface, 4. Driver left buffer box, 5. Driver right buffer box, 6. Driver adjustment mechanism, 7. Make-up heater right steam outlet, 8. Make-up heater left steam outlet, 9. Make-up heater left buffer box, 10. Make-up heater right buffer box, 11. Make-up heater left collecting box, 12. Make-up heater right collecting box, 13. Make-up heater high-pressure steam interface.

[0023] Figure 3 Middle: 14. Driver manifold, 15. Driver left nozzle, 16. Driver right nozzle, 17. Exhaust steam collecting chamber, 18. Driver right nozzle, 19. Driver left nozzle, 20. Driver left buffer chamber, 21. Driver right buffer chamber, 22. Driver adjustment rod, 23. Driver left sealing gasket, 24. Driver right sealing gasket, 25. Driver left sealing fastener, 26. Driver right sealing fastener.

[0024] Figure 4 Middle: 27. Compensator manifold, 28. Compensator left nozzle, 29. Compensator right nozzle, 30. Compensator left nozzle, 31. Compensator right nozzle, 32. Compensator left collecting chamber, 33. Compensator right collecting chamber, 34. Compensator left steam discharge chamber, 35. Compensator right steam discharge chamber, 36. Compensator left buffer chamber, 37. Compensator right buffer chamber.

[0025] Figure 5 Middle: The bold line in the figure indicates the steam operation pipeline, A. driver controls the cut-off valve, B. compensator controls the cut-off valve, C. the device of the present invention, D. the left external temperature heating chamber, E. the right external temperature heating chamber, F. the temperature and pressure balancer, G. the left external temperature sensor, H. the right external temperature sensor, L. the steam circulation pipeline, and M. the condensate drain cut-off valve. DETAILED DESCRIPTION

[0026] The device of the present invention is mainly composed of Figure 1 The circulating driver S1 and the temperature compensator S2 are composed of components and are installed in the parallel heating pipeline of the vulcanization external temperature. Figure 5 The position of C in the figure, its appearance three-view drawing is as follows Figure 2 shown.

[0027] The circulation driver S1 is composed of the driver high-pressure steam interface, the driver splitter plate, the driver left and right nozzles, the tail steam collection box, the driver left and right buffer boxes, the left and right sealing fasteners, and the adjustment mechanism. Its structural composition is as follows: Figure 1 and Figure 3As shown, the driver left nozzle 15 and the driver right nozzle 16 in the driver S1 are symmetrical on both sides of the driver diverter plate 14. The driver diverter plate 14 divides the inner cavity of the driver high-pressure steam interface 1 into two steam flow channels. The high-pressure steam inlets of the left and right nozzles of the driver are respectively tightly connected with the two formed steam flow channels. The left and right nozzles of the driver share a tail steam collecting box 2 and a driver high-pressure steam interface 1. The lumen of the driver high-pressure steam interface 1 is tightly sealed and connected with the tail steam collecting box 2, the diverter plate 14, and the left and right nozzles. A tail steam interface 3 is opened on the side of the tail steam collecting box 2. The tail steam interface 3 is located on the symmetrical central axis of the left and right nozzles of the driver. The tail steam interface 3 is used to connect the tail steam circulation pipeline in the parallel heating system. Two holes are opened at the bottom of the tail steam collecting box for installing the left buffer box 4 and the right buffer box 5 of the driver, and are respectively concentric with the left nozzle 19 of the driver and the right nozzle 18 of the driver. The sealing fastener 25 is connected to the left hole at the bottom of the exhaust steam collecting box 2 by means of a thread. The left sealing fastener 25 squeezes the left sealing gasket 23 by means of a thread, so that the left sealing gasket 23 is deformed to seal the gap between the left buffer box 4 of the driver and the left hole at the bottom of the exhaust steam collecting box 2. The right sealing fastener 26 is connected to the right hole at the bottom of the exhaust steam collecting box 2 by means of a thread. The right sealing fastener 26 squeezes the right sealing gasket 24 by means of a thread, so that the right sealing gasket 24 is deformed to seal the gap between the right buffer box 5 of the driver and the right hole at the bottom of the exhaust steam collecting box 2. Steam exhaust ports are provided on the sides of the left and right buffer boxes of the driver, which are respectively used to connect the steam collection interfaces of the left and right collection boxes of the compensator. The relative position of the bottom of the exhaust steam collecting box 2 and the bottom of the left and right buffer boxes of the driver is limited by an adjusting screw 22, and an adjusting mechanism 6 is installed. The adjusting mechanism 6 is used to adjust and fix the relative distance between the upper openings of the left and right buffer boxes of the driver and the left and right nozzles of the driver.

[0028] The compensator S2 is composed of a compensator high-pressure steam interface, a compensator diverter plate, a compensator left and right nozzles, a compensator left and right collection box, and a compensator left and right buffer box. Its structural components are as follows: Figure 1 and Figure 4As shown, the left and right nozzles 28 and 29 of the compensator S2 are symmetrically arranged on both sides of the compensator manifold 27. The compensator manifold 27 divides the inner cavity of the compensator high-pressure steam interface 13 into two steam flow channels. The high-pressure steam inlets of the left and right nozzles of the compensator are tightly connected with the two formed steam flow channels respectively. The left and right nozzles of the compensator share a compensator high-pressure steam interface 13. The lumen of the compensator high-pressure steam interface 13 is tightly sealed and connected with the left and right collecting boxes 11, 12, the compensator manifold 27 and the left and right nozzles. The sides of the left and right collecting boxes 11 and 12 are respectively provided with collecting interfaces. The steam outlet interface on the side of the left and right buffer boxes of the driver is connected. The left buffer box 9 and the right buffer box 10 of the compensator are connected to the bottom of the left collecting box 11 and the right collecting box 12 of the compensator respectively, and the opening is an arc or conical structure. The opening of the left buffer box 9 of the compensator is concentric with the left nozzle 30 of the compensator, and the opening of the right buffer box 10 of the compensator is concentric with the right nozzle 31 of the compensator. The sides of the left buffer box 9 and the right buffer box 10 of the compensator are respectively provided with a left steam outlet 8 and a right steam outlet 7. The left steam outlet 8 is used to connect the steam inlet pipeline of the left heating chamber of the parallel heating system, and the right steam outlet 7 is used to connect the steam inlet pipeline of the right heating chamber of the parallel heating system.

[0029] The operation process of heating steam in the device of the present invention and the results of CFD simulation:

[0030] If the actual measured temperature of the heating steam in the heating device meets the process requirement range or a preset range, it means that the heating system only needs to maintain the circulation operation of the steam and only needs to appropriately supplement the loss of the steam circulation. At this time, the heating system only opens the high-pressure steam entering the high-pressure interface 1 of the driver to allow the high-pressure steam to enter the circulation driver S1. The entering high-pressure steam is respectively introduced into the left nozzle 15 and the right nozzle 16 of the driver through the driver diverter plate 14, and forms a high-speed steam flow at the left nozzle 19 and the right nozzle 18 of the driver respectively. The high-speed steam flow formed by the left nozzle 19 of the driver draws the sulfide tail steam entering the tail steam collecting chamber 17 from the tail steam interface and is injected into the left buffer chamber 20 of the driver. The entering high-speed jet steam is buffered and the kinetic energy is reduced in the left buffer chamber 20 of the driver. The steam with reduced kinetic energy then enters the left collecting chamber of the compensator from the steam outlet on the side of the left buffer chamber 20. In the collecting cavity 32, the steam in the left collecting cavity 32 of the compensator enters the left buffer cavity 36 of the compensator through the bottom channel. Finally, the steam is discharged from the steam outlet on the side of the left buffer cavity 36 of the compensator and enters the left vulcanization heating cavity of the parallel heating system for heating operation; at the same time, the high-speed steam flow formed by the right nozzle 18 of the driver also draws the vulcanized tail steam in the tail steam collecting cavity 17 and injects it into the right buffer cavity 21 of the driver. The entering high-speed jet steam is buffered and the kinetic energy is reduced in the right buffer cavity 21 of the driver. The steam with reduced kinetic energy enters the right collecting cavity 33 of the compensator from the steam outlet on the side of the right buffer cavity 21 of the driver. The steam in the right collecting cavity 33 of the compensator enters the right buffer cavity 37 of the compensator through the bottom channel. Finally, the steam is discharged from the steam outlet on the side of the right buffer cavity 37 of the compensator and enters the right vulcanization heating cavity of the parallel system for heating operation. Its CFD simulation operation is as follows: Figure 6 As shown, Figure 6 The figure shows the running trajectory of the steam in the device of the present invention and the equipotential cross-section diagram of the speed and pressure in the circulation driver S1 and the compensator S2 when only the circulation of the steam in the parallel heating system is maintained. It can be seen from the figure that the left and right steam speeds output after the steam passes through the device of the present invention are very low, the pressure is stable, and no eddy current is generated when the steam enters the heating chamber, which can ensure the smooth circulation of the steam in the two parallel heating chambers.

[0031] If the temperature of the heating steam is lower than the minimum value of the process requirement range or a preset low value, it means that the steam heat in the heating system is insufficient and more steam needs to be added quickly. At this time, the heating system also opens the high-pressure steam entering the compensator S2, so that the high-temperature steam enters the compensator S2 through the compensator high-pressure steam interface 13. The entering high-pressure steam is respectively introduced into the compensator left nozzle 28 and the compensator right nozzle 29 through the compensator diverter plate 27, and forms a high-speed steam flow at the compensator left nozzle 30 and the compensator right nozzle 31 respectively. The high-speed steam flow formed at the compensator left nozzle 30 draws the steam in the compensator left collecting chamber 32 and is injected into the compensator left buffer chamber 32. In the punching cavity 36, the high-speed jet steam is buffered and the kinetic energy is reduced in the left buffer cavity 36 of the compensator. The steam with reduced kinetic energy is discharged from the left steam outlet cavity 34 on the side of the left buffer cavity 36 of the compensator and enters the left vulcanization heating cavity of the parallel system for heating operation; the high-speed steam flow formed by the right nozzle 31 of the compensator draws the steam in the right collecting cavity 33 of the compensator and is injected into the right buffer cavity 37 of the compensator. The high-speed jet steam is buffered and the kinetic energy is reduced in the right buffer cavity 37 of the compensator. The steam with reduced kinetic energy is discharged from the right steam outlet cavity 35 on the side of the right buffer cavity 37 of the compensator and enters the right vulcanization heating cavity of the parallel system for heating operation. Its CFD simulation operation is as follows: Figure 7 As shown, Figure 7 The figure shows the running trajectory of the steam in the device of the present invention and the equipotential cross-section diagram of its speed and pressure in the circulation driver S1 and the compensator S2 when the parallel heating system needs to heat up quickly. It can be seen from the figure that the kinetic energy of the left and right steam output after the steam passes through the device of the present invention is very low, the pressure is stable, and no eddy current is generated when the steam enters the heating chamber. When the system quickly replenishes the steam heat, the steam also circulates smoothly in the two parallel heating chambers.

[0032] The operation of the device of the present invention in the entire external temperature parallel heating system is described as follows. The thermal pipeline of the heating system is as follows: Figure 5 As shown:

[0033] When the left external temperature sensor G or the right external temperature sensor H detects that the external temperature is lower than the process requirement range or a predetermined low value, the steam circulation driver controls the shut-off valve A and the compensator controls the shut-off valve B to open simultaneously, so that more steam can enter the entire external temperature heating circulation system through the two groups of jet nozzles of the device of the present invention at the same time. The steam entering enters the left external temperature heating chamber D and the right external temperature heating chamber E through the steam inlet pipeline from the left and right steam outlets of the device C of the present invention to provide heat at the same time. After the heat of the left external temperature heating chamber D and the right external temperature heating chamber E is used, the steam enters the left and right interfaces of the temperature-pressure balancer F through their respective tail steam pipelines. The sulfide tail steam coming out of the temperature-pressure balancer F is returned to the heating system for use again through the circulation pipeline L. The condensed water precipitated from the steam in the heating system passes through the liquid level control circuit. The condensate discharge cut-off valve M controlled by the control discharges; when the left external temperature sensor G and the right external temperature sensor H detect that the external temperature is within the process standard value range or the preset range, the steam circulation driver controls the cut-off valve A to open and the heating compensator cut-off valve B to close, so that the incoming high-pressure steam only drives the circulation flow of the heating steam and appropriately supplements the loss of steam in the circulation. The circulation flow process of the steam in the heating system is the same as the previous description; when the left external temperature sensor G or the right external temperature sensor H detects that the external temperature exceeds the maximum value of the process requirement range, the steam circulation driver controls the cut-off valve A and the compensator controls the cut-off valve B to close, waiting for the steam in the parallel heating system to naturally lose temperature and cool down until the temperatures detected by the left external temperature sensor G and the right external temperature sensor meet the process requirement range.

Claims

1. A heating steam circulation drive device in a parallel heating system, comprising a circulation drive and a temperature compensator, characterized in that: The circulation drive and the compensating temperature device have jet devices with similar structural forms, which are respectively composed of a collection box, a nozzle, and a buffer box as main components, but the sizes and forms of each component are different. They are combined by connecting the steam outlet of one of the buffer boxes to the steam inlet of another collecting box.

2. The circulating drive according to claim 1, characterized in that: The circulation drive is composed of a collection box, a left nozzle, a right nozzle, a high-pressure steam interface, a diverter baffle, a left sealing fastener, a right sealing fastener, a left buffer box, a right buffer box and an adjusting mechanism. The diverter baffle divides the inner cavity of the high-pressure steam interface into two steam flow channels. The left nozzle and the right nozzle are tightly and symmetrically connected to the two flow channels respectively. The collection box symmetrically wraps the left and right nozzles and forms a common chamber with the left and right nozzles. The upper side of the opening of the inner cavity of the collection box is completely tangent to the outer sides of the left and right nozzles and is sealed. A circulating steam inlet is provided on the side of the collection box at the symmetrical midline position of the left and right nozzles. Two openings for installing the left and right buffer boxes are opened at the bottom of the collection box, and the openings are directly opposite to the nozzles of the left and right nozzles. , and are concentric with the left and right nozzles respectively. The upper parts of the left and right buffer boxes are cylindrical and can extend into the hole at the bottom of the collecting box. The openings are arc-shaped or conical structures and are concentric with the holes at the bottom of the collecting box respectively. The lower parts of the left and right buffer boxes are cavities with larger volumes. A circulating steam outlet is provided on the side of the cavity. The left and right sealing fasteners are respectively connected to the openings at the bottom of the collecting box through threads. The sealing gasket is tightened and squeezed through the threads to deform the sealing gasket to seal the connection gap between the buffer box and the collector. The adjustment mechanism is symmetrically fixedly installed at the bottom of the left and right buffer boxes. The relative position between the openings of the left and right buffer boxes and the left and right nozzles is adjusted by the adjustment rod and threads provided at the bottom of the collector, and fixed with inner and outer nuts.

3. The compensator according to claim 1, characterized in that: The compensating temperature device is composed of a left collecting box, a right collecting box, a left nozzle, a right nozzle, a high-pressure steam interface, a diverter baffle, a left buffer box and a right buffer box as components. The diverter baffle divides the high-pressure steam interface cavity into two steam flow channels. The left nozzle and the right nozzle are tightly and symmetrically connected to the two flow channels respectively. The upper inner cavity openings of the left collecting box and the right collecting box are tangent to the outer sides of the left and right nozzles and sealed. The bottoms of the left and right collecting boxes are provided with openings for connecting to the buffer boxes, and the openings are arc-shaped or conical structures. The openings are concentric with the nozzles of the corresponding nozzles. The sides of the left and right collecting boxes are respectively provided with circulating steam inlets. The upper part of the buffer box is a cylindrical open cavity, and the openings are tangent to and tightly connected to the openings at the bottom of the corresponding collecting box. The lower part of the buffer box is a cavity with a larger volume, and a circulating steam outlet is provided on the side of the cavity.

4. The heating steam circulation driving device in the parallel heating system according to claim 1, characterized in that: The circulating drive and the collecting box in the circulating drive components are not limited to the left and right nozzles sharing a collecting box and a circulating steam inlet, and include forms such as the collecting box in the compensator, where the left and right nozzles each independently use a collecting box and an independent circulating steam inlet.

5. The heating steam circulation driving device in the parallel heating system according to claim 1, characterized in that: The circulation drive and compensator are not limited to the front-to-back order, that is, the jet device installed in the front can be used as a circulation drive, and the jet device installed in the back can be used as a compensator. At the same time, the jet device installed in the back can also be used as a steam circulation drive, and the jet device installed in the front can be used as a compensator.

6. The heating steam circulation driving device in the parallel heating system according to claim 1, characterized in that: The installation and connection method of the left and right buffer boxes and the left and right collection boxes in the described compensator is not limited to a fixed tight connection, and includes structural forms such as the adjustable connection and installation form of the left and right buffer boxes and the collector in the described driver.

7. The heating steam circulation driving device in the parallel heating system according to claim 1, characterized in that: The circulating steam inlet and circulating steam outlet provided in the collecting box and the buffer box in the circulating driver and the compensating temperature device are not limited to fixed directions and angles of connection with each other.

8. The heating steam circulation driving device in the parallel heating system according to claim 1, characterized in that: The components of the circulation drive and the temperature compensator are not limited to specific sizes and shapes, including deformations of various shapes and changes in sizes of the components.

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