A dual-axis rotary drum and dough mixer jacket cooling device

Abstract

This invention discloses a dual-axis rotary drum and noodle machine jacket cooling device, belonging to the technical field of cooling devices. It includes a frame with two main shafts symmetrically rotatably connected to its inner side; it also includes a tilting motor mounted on the frame; and a tilting frame fixedly connected between the two main shafts at their closest ends and driven by the tilting motor's power output, enabling reciprocating tilting and unloading actions under the motor's drive. This invention, by setting multiple flow-guiding baffles within the cooling jacket chamber, divides the originally wide single jacket into multiple independent heat exchange sub-chambers. Utilizing series-connected components arranged with spatial staggers on adjacent baffles, the natural flow inertia of the fluid is broken. The cooling medium is forced to flow in a meandering and reversible manner between the sub-chambers, forming a series of deflected flow paths. This allows the refrigerant to flush all parts of the inner liner's outer wall, completely eliminating fluid short-circuiting and stagnant dead zones, thus improving the convective heat transfer effect.

Description

Technical Field

[0001] This invention relates to the field of cooling device technology, specifically to a dual-axis rotary drum and noodle machine sandwich cooling device. Background Technology

[0002] Twin-shaft rotary dough mixers are core equipment in modern industrialized production lines for pasta, baked goods, and frozen foods. During production, two parallel mixing shafts forcefully compress, stretch, and knead the dough inside the drum. Due to the intense internal friction generated by the dough under complex mechanical forces, and the exothermic hydration reaction accompanying the formation of the gluten network, a large amount of heat is generated inside the dough mixer drum, especially in the high-shear area where the two shafts intersect. If this heat cannot be dissipated in time, the dough temperature will rise rapidly. This not only destroys the normal biological activity of yeast but also causes gluten protein denaturation, resulting in sticky and broken dough, severely reducing the quality and batch stability of the final product.

[0003] To control dough temperature rise, existing heavy-duty dough mixers typically have cooling devices installed on the outside of the drum. The mainstream approach involves placing an outer sleeve over the inner drum of the mixer, creating a closed cooling jacket between them. During operation, a water pump circulates a cooling medium, such as room temperature water or a mixture of ice and water, into the cooling jacket. The flow of this cooling medium within the jacket absorbs the heat transferred from the inner drum, thereby cooling the dough.

[0004] However, existing cooling devices have obvious fluid dynamic defects in practical applications. Ordinary cooling jackets are often a huge, continuous annular cavity or only have simple flow channels. Fluids have the physical nature of seeking advantages and avoiding disadvantages. After entering the jacket, the cooling medium will automatically seek the straight path of least resistance to flow to the outlet, thus forming a shortcut flow (short-circuit flow). This phenomenon causes the cooling medium to be unable to effectively flush various areas of the cylinder, forming a large area of ​​fluid stagnation zone (heat exchange dead zone) inside the jacket. The heat in these dead zone areas cannot be carried away, resulting in extremely uneven temperature distribution on the inner wall of the cylinder. Summary of the Invention

[0005] The purpose of this invention is to provide a cooling device for a dual-axis rotary dough mixer, which uses a flow guide baffle and a staggered connecting component to force the refrigerant to form a series of baffle paths in the interlayer, completely eliminating heat exchange dead zones and achieving efficient global cooling of the dual-axis rotary dough mixer.

[0006] To solve the above-mentioned technical problems, the technical solution adopted by the present invention is as follows:

[0007] This invention provides a dual-axis rotary dough mixer with a sandwich cooling device, comprising a frame with two main shafts symmetrically rotatably connected to its inner side; further comprising: a tilting motor mounted on the frame; a tilting frame fixedly connected between the two main shafts at their closest points and connected to the power output end of the tilting motor; and a dough mixer drum fixedly mounted on the tilting frame, the drum comprising an inner liner and an outer sheath covering the inner liner, the outer wall of the inner liner and the inner wall of the outer sheath forming a sealed cooling sandwich chamber; the cooling sandwich chamber flows along the overall direction of the refrigerant flow. The machine has a main refrigerant inlet at the front end that connects to the external refrigerant supply and a main refrigerant outlet at the rear end. Multiple flow guide baffles are spaced apart within the cooling jacket cavity, dividing it into several heat exchange sub-cavities arranged sequentially along the axial direction of the dough mixer cylinder. Multiple series-connecting components are installed axially along the outer wall of the outer sheath, spanning the corresponding flow guide baffles, to connect two adjacent heat exchange sub-cavities for refrigerant series flow. The flow ports of two adjacent series-connecting components connected to the same heat exchange sub-cavity are staggered in spatial projection.

[0008] By adopting the above technical solution, multiple flow guide baffles are set in the cooling jacket cavity, which cuts the originally wide single jacket into multiple independent heat exchange sub-cavities. The series connection components arranged in a spatially staggered manner on the adjacent baffles break the natural flow inertia of the fluid. The cooling medium is forced to flow in a detour and backflow between the sub-cavities, forming a series of deflected flow paths. This allows the refrigerant to flush all parts of the outer wall of the inner tank, completely eliminating fluid short circuits and stagnant dead zones, and greatly improving the convective heat transfer effect.

[0009] A further improvement of the technical solution of this invention is that: parallel direct supply pipes are arranged axially on the outer wall of the outer sheath; the series connection assembly includes: a mounting plate; an adjusting cylinder, fixed to the side of the mounting plate away from the outer sheath by a reset bracket; a valve core, axially slidably connected to the inner wall of the adjusting cylinder, with two annular grooves spaced apart on the outer circumferential surface of the valve core; two series pipes, connected to the cylinder wall of the adjusting cylinder, the two series pipes respectively connecting to two adjacent heat exchange sub-chambers; along the flow direction of the refrigerant, the two adjacent heat exchange sub-chambers are respectively defined as the upstream heat exchange sub-chamber and the downstream heat exchange sub-chamber; two parallel pipes, connected to the cylinder wall of the adjusting cylinder, and the two... The connection points of the parallel pipes on the regulating cylinder wall and the connection points of the two series pipes are distributed at intervals along the axial direction of the regulating cylinder. One of the parallel pipes is connected to the downstream heat exchange sub-chamber, and the other parallel pipe is connected to the parallel direct supply pipe. One-way valves are installed in both the series pipe and the parallel pipe connected to the downstream heat exchange sub-chamber. A valve stem is fixedly connected to one end of the valve core. A thermal triggering structure is provided on the side of the mounting plate facing the downstream heat exchange sub-chamber. The valve stem passes through the reset frame and the mounting plate and is drivenly connected to the thermal triggering structure. The thermal triggering structure is configured such that when an abnormally high temperature is detected in the refrigerant in the downstream heat exchange sub-chamber, it drives the valve stem to cause axial displacement of the valve core.

[0010] By adopting the above technical solution, and through the combination of redundant parallel direct supply pipes and mixed flow control structure, the problem of cooling failure of the terminal heat exchange sub-chamber caused by the continuous heat absorption of the refrigerant along the process in a pure series cooling water circuit is effectively solved. When a heat exchange sub-chamber experiences abnormally high temperature due to localized severe friction of the dough, the thermal trigger structure can spontaneously sense the change in fluid temperature and drive the valve core to generate axial displacement, thereby changing the alignment state of the annular groove and the pipeline. This linkage mechanism reduces or cuts off the inflow of the upstream series refrigerant carrying heat, while simultaneously opening the channel of the parallel direct supply pipe, allowing fresh low-temperature refrigerant that has not undergone prior heat exchange to be directly injected into the overheated heat exchange sub-chamber, thereby quickly and directly suppressing local temperature rise and ensuring the uniformity and stability of the global temperature distribution of the dough mixer cylinder.

[0011] A further improvement of the technical solution of the present invention is as follows: the thermal triggering structure includes a temperature-sensing shell that is sealed and fixed to the side of the mounting plate facing the downstream heat exchange sub-chamber, the temperature-sensing shell extending into the interior of the downstream heat exchange sub-chamber to be immersed in the refrigerant; the interior of the temperature-sensing shell is sealed and filled with a thermal expansion medium; an elastic isolation member is fixedly connected inside the temperature-sensing shell, one end of the valve stem extends into the unclosed opening end of the temperature-sensing shell and movably abuts against the elastic isolation member, the elastic isolation member completely seals and encloses the thermal expansion medium inside the temperature-sensing shell; the elastic isolation member separates the thermal expansion medium from the valve stem; a force-bearing boss is fixedly connected to the valve stem at the location of the reset frame, and a reset spring is sleeved on the outside of the valve stem, the two ends of the reset spring abutting against the inner wall of the reset frame and the force-bearing boss respectively.

[0012] A further improvement of the technical solution of this invention lies in the fact that the huge volume expansion force generated by the thermal phase change of the thermosensitive expansion medium is used as a mechanical driving source. Combined with the force transmission and sealing effect of the elastic isolation component, it can not only stably output a thrust sufficient to overcome the water pressure of the system, but also eliminate the risk of leakage of the liquid expansion medium. This fully enclosed mechanical structure does not require an external power supply or a complex electronic temperature sensor. In the harsh industrial environment of high dust and high humidity encountered during the operation of the dual-axis dough kneading machine, it has extremely high operational stability, anti-interference ability and extremely low maintenance cost.

[0013] A further improvement of the technical solution of the present invention is that: the dough mixer cylinder has an upright dough mixing state and an inverted unloading state after being rotated 180°; each heat exchange sub-chamber is connected to a drain branch pipe at its physical top when it is in the upright dough mixing state, and a buoyancy valve assembly is installed inside the drain branch pipe; the buoyancy valve assembly is configured to control the opening and closing of the drain branch pipe according to the rise and fall of the liquid level in the heat exchange sub-chamber when it is in the upright dough mixing state.

[0014] By adopting the above technical solution, a buoyancy valve assembly controlled by liquid level is installed on the physical top of each heat exchange sub-chamber when it is in the upright state, realizing the passive automatic venting function of the system. It can use the buoyancy of the fluid itself and the liquid level change as the driving source. When gas accumulates, it automatically opens the venting path and automatically resets the seal after the gas is vented. This ensures that the heat exchange sub-chamber is always filled with refrigerant, maintains the expected heat exchange area, and does not require manual intervention or the introduction of additional electrical control nodes. It meets the fluid pressure maintenance and anti-gas lock requirements of the dough mixer in the upright operation state.

[0015] A further improvement of the technical solution of the present invention is as follows: a return water main pipe connected to the external refrigerant recovery end is provided axially on the outer wall of the outer sheath; each drain branch pipe is connected to the return water main pipe; the buoyancy valve assembly includes an end cap fixedly connected to one end of the drain branch pipe, an end seat fixedly connected inside the end cap, a linkage rod inserted through the middle of the end seat, a plug fixedly connected to one end of the linkage rod, and a float fixedly connected to the other end of the linkage rod extending into the interior of the heat exchange sub-chamber; a sealing part is formed by a protrusion on the inner wall of the drain branch pipe, and a conical sealing slope is provided on the end face of the plug facing the sealing part, the conical sealing slope abutting against the sealing part to form an end face seal; a ring seat is fixedly connected inside each drain branch pipe, a guide rod is slidably connected to the middle of the ring seat, one end of the guide rod is fixedly connected to the plug, and a limit head is fixedly connected to the other end; a control spring is sleeved on the outside of the guide rod, and the two ends of the control spring abut against the plug and the ring seat respectively.

[0016] By employing the above technical solution, the adaptive action of the dual-guided buoyancy valve assembly under different equipment postures effectively solves the problems of high back pressure and energy consumption in the pipeline network during the unloading idle period of the continuous cooling system. When the dough mixer cylinder flips to the inverted unloading state, the drain branch pipe also inverts to the bottom. The buoyancy force of the refrigerant on the float and the elastic force of the control spring are superimposed in the same direction along the valve body axis, jointly driving the plug to disengage from the sealing part. When the equipment is inverted, the drain channels between each heat exchange sub-chamber and the return water main are passively and forcibly opened, instantly switching the originally series high-resistance pipeline network to multiple parallel low-resistance bypass pipelines. This design allows the external chiller and water pump to maintain basic refrigerant flow with extremely low system back pressure without shutting down or interrupting the circulation. This avoids frequent start-ups and shutdowns of the refrigeration equipment, effectively reduces the standby energy consumption of the water pump, and removes residual heat from the cylinder metal through continuous low-resistance circulation. It also keeps the cooling jacket fully filled with refrigerant, ensuring that the equipment can seamlessly transition to high-intensity cooling mode when returning to center for the next batch of dough kneading operations.

[0017] A further improvement of the technical solution of the present invention is as follows: the refrigerant inlet is connected to the parallel direct supply pipe; the refrigerant outlet is connected to the return water main pipe; hollow flow channels extending axially are opened inside both main shafts, and radial through holes communicating with the hollow flow channels are opened on the outer wall of the main shafts; sleeve-type rotary joints are fitted on the outer walls of both main shafts, the sleeve-type rotary joints include a stationary stator outer ring, and an annular liquid collection cavity is formed between the inner wall of the stator outer ring and the outer wall of the main shaft, the annular liquid collection cavity always communicating with the radial through holes during the rotation of the main shaft; the hollow flow channel inside the main shaft located on one side is connected to the return water main pipe, and an external port for communicating with the external refrigerant recovery end is provided on the stator outer ring fitted on the main shaft on that side; the hollow flow channel inside the main shaft located on the other side is connected to the parallel direct supply pipe, and an external port for communicating with the external refrigerant supply end is provided on the stator outer ring fitted on the main shaft on that side.

[0018] By employing the above technical solution, a rigid fluid transition channel is constructed between the external stationary pipeline and the moving cylinder by installing a sleeve-type rotary joint on the outer wall of the main shaft and cooperating with the hollow flow channel inside the main shaft, while avoiding the mechanical transmission and support space at the end of the main shaft. The stator outer ring remains stationary to connect with the external pipeline, and its internal annular liquid collecting cavity covers the outer wall of the main shaft, ensuring that the radial through hole remains connected to the liquid cavity when the main shaft rotates 180°, completely eliminating the risk of entanglement and fatigue fracture of the flexible hose caused by equipment rotation.

[0019] A further improvement of the technical solution of the present invention is that: the outer surface of the outer sheath is fully covered with a cryogenic insulation layer, and a protective shell for protecting the appearance of the equipment is provided on the outside of the cryogenic insulation layer; the protective shell and the outer sheath are connected and supported by multiple non-metallic heat-insulating support blocks distributed at intervals.

[0020] By adopting the above technical solution, a non-metallic thermal insulation support block is set between the outer sheath and the protective shell, effectively cutting off the solid heat conduction path between the inner and outer metal structures, thus constructing a physically broken bridge thermal insulation system. Combined with the full coverage of the cryogenic insulation layer, this structure completely isolates the cooling interlayer chamber from the external environment while ensuring the mechanical support strength of the protective shell. This significantly reduces the unnecessary energy loss of the refrigeration system to the environment and enables the overall surface temperature of the protective shell to be stably maintained above the environmental dew point. This eliminates the phenomenon of condensation and dripping water on the outer surface of the equipment from the root, and meets the clean production requirements of high-humidity food processing environments.

[0021] A further improvement of the technical solution of the present invention is that: two stirring shafts are arranged in parallel and rotating manner inside the inner liner; the bottom cross section of the inner liner is a W-shaped structure adapted to the two stirring shafts, and the bottom center of the W-shaped structure has an upwardly protruding saddle part corresponding to the high shear zone where the two stirring shafts intersect; the bottom of the outer sheath and the bottom edge contour of the multiple flow guide baffles are all in a contoured undulating structure adapted to the W-shaped structure.

[0022] By adopting the above technical solution, the bottom of the outer sheath and the bottom edge contour of the multiple flow guide baffles are designed to conform to the "W"-shaped structure of the inner liner, thus constructing a constant cross-section cooling channel that closely follows the outer wall of the saddle section. In actual operation, this conformal structure is like a mold, forcing the cooling medium to climb up the slope along the saddle section and cross the raised area when flowing through the bottom of the heat exchange chamber. This allows for high-velocity forced convection flushing and heat exchange in the core high-heat area, completely eliminating the heat accumulation below the saddle section and ensuring the temperature stability of the high-shear zone of the dough.

[0023] A further improvement of the technical solution of the present invention is that: a load-bearing support plate is coaxially fixedly sleeved on the outside of both main shafts; auxiliary support components that cooperate with the load-bearing support plate are provided on the bottom of both sides of the frame to share the radial heavy load when the dough kneading machine cylinder is fully loaded and overturned; each auxiliary support component includes a set of two parallel auxiliary support wheels, which are symmetrically distributed and rotatably connected to the frame.

[0024] By adopting the above technical solution, a cradle-type lifting structure similar to a heavy-duty rotary kiln is constructed by adding a load-bearing support plate to the outside of the main shaft and configuring an auxiliary support assembly consisting of two parallel auxiliary support wheels at the bottom of the frame. This not only significantly reduces the radial stress borne by the end of the main shaft, ensuring the absolute straightness and joint sealing of the main shaft during rotation, but also provides extremely high mechanical stability for the 180° reciprocating rotation of the equipment, avoiding left and right swaying of the equipment during rotation and high-load kneading.

[0025] By adopting the above technical solution, the technical effects achieved by this invention compared to the prior art are as follows:

[0026] 1. This invention provides a dual-axis rotary drum and noodle machine jacket cooling device. By setting multiple flow guide baffles and staggered series-connected components in the cooling jacket cavity, the refrigerant is forced to form a tortuous and reversible series flow path, which completely eliminates the fluid short circuit and heat exchange dead zone of the traditional cavity jacket, and significantly improves the overall cooling and heat exchange efficiency of the inner liner of the drum.

[0027] 2. This invention provides a dual-axis rotary drum and dough machine sandwich cooling device. By setting a mechanical thermally sensitive mixing and control structure, it can automatically conduct parallel direct supply pipes for targeted strong cooling when abnormal high temperatures occur in this area. This effectively overcomes the problem of refrigerant heat attenuation along the flow path caused by pure series flow channels, ensures the uniformity of the overall temperature of the dough, and does not require external electrical control equipment, thus having extremely strong anti-interference ability.

[0028] 3. This invention provides a cooling device for a dual-axis rotary drum dough mixer, utilizing a dual-guide buoyancy valve assembly adaptively controlled by liquid level and equipment posture. This assembly achieves automatic venting and pressure maintenance during upright dough mixing, and forcibly opens a low-resistance parallel bypass pipeline during inverted unloading. This design not only accelerates the evacuation of residual refrigerant but also allows an external industrial chiller unit to maintain low-resistance circulation without shutting down, avoiding frequent compressor start-ups and shutdowns and high back pressure energy consumption of the water pump.

[0029] 4. This invention provides a dual-axis rotary drum and noodle machine jacket cooling device. By utilizing the dynamic-static conversion pipeline network of the hollow main shaft and the sleeve-type rotary joint, a stable and reliable rigid fluid transition channel is constructed under the premise of avoiding interference between the transmission and support at the end of the main shaft. This eliminates the hidden dangers of flexible inlet and outlet water hoses easily getting tangled and fatigued when the equipment is rotated 180°.

[0030] 5. This invention provides a cooling device for a dual-axis rotary drum dough mixer, which features a bottom-conforming cooling design for the "W"-shaped saddle section of the dual-axis dough mixer, which is prone to overheating, to achieve forced flushing of the core hot spots. At the same time, in conjunction with non-metallic thermal break support and an external heavy-duty cradle-type support structure, it not only solves the problem of condensation and dripping water on the outer shell of the high-humidity workshop from the root, but also significantly reduces the radial force on the main shaft, avoiding the bending deformation of the main shaft under heavy load and overturning. Attached Figure Description

[0031] The invention will now be further described with reference to the accompanying drawings.

[0032] Figure 1 This is a schematic diagram of the overall structure of the present invention from a first-view perspective;

[0033] Figure 2 This is a schematic diagram of the overall structure of the invention from a second perspective;

[0034] Figure 3 This is a three-dimensional structural diagram of the dough mixer cylinder and the pipes installed thereon according to the present invention.

[0035] Figure 4 This is a schematic diagram illustrating the refrigerant flow principle of the present invention;

[0036] Figure 5 This is a cross-sectional view of the main shaft and sleeve-type rotary joint of the present invention.

[0037] Figure 6 This is a side sectional view of the overall structure of the present invention;

[0038] Figure 7 This is a schematic diagram of the external structure of the series-connected component of the present invention;

[0039] Figure 8 This is a three-dimensional cross-sectional view of the series-connected component of the present invention;

[0040] Figure 9 This is a schematic diagram of the front cross-sectional structure of the series-connected component of the present invention;

[0041] Figure 10 This is a schematic diagram of the external structure of the buoyancy valve assembly of the present invention;

[0042] Figure 11 This is a three-dimensional cross-sectional view of the buoyancy valve assembly of the present invention;

[0043] Figure 12 This is a schematic diagram showing the disassembled structure of the buoyancy valve assembly of the present invention;

[0044] Figure 13 This is a structural schematic diagram of the entire invention from a third-person perspective.

[0045] In the diagram: 1. Frame; 10. Main return water pipe; 11. Parallel direct supply pipe; 12. Sleeve-type rotary joint; 121. Stator outer ring; 122. Annular liquid collection chamber; 123. External port; 13. Auxiliary support wheel; 14. Load-bearing support plate; 15. Outer sheath; 16. Cryogenic insulation layer; 17. Flow guide baffle; 18. Inner liner; 19. Protective shell; 2. Tilting motor; 3. Main shaft; 301. Hollow flow channel; 302. Radial through hole; 4. Tilting frame; 5. Dough mixer cylinder; 6. Refrigerant main inlet; 7. Refrigerant main outlet; 8. Series connection assembly; 801. Adjusting cylinder 802. Valve core; 803. Annular groove; 804. Series pipe; 805. Parallel pipe; 806. Reset bracket; 807. Mounting plate; 811. Temperature sensing housing; 812. Thermosensitive expansion medium; 813. Elastic isolation element; 814. Valve stem; 815. Force-bearing boss; 816. Reset spring; 9. Buoyancy valve assembly; 901. Drainage branch pipe; 902. End seat; 903. Linkage rod; 904. Plug; 905. Float; 906. Guide rod; 907. Control spring; 908. Ring seat; 909. Limit head; 910. Sealing part; 911. End cap. Detailed Implementation

[0046] The present invention will be further described in detail below with reference to the embodiments.

[0047] Example 1

[0048] like Figures 1-13As shown, this invention provides a dual-axis rotary drum dough mixer with a sandwich cooling device, including a frame 1 with two main shafts 3 symmetrically rotatably connected to its inner side; it also includes: a tilting motor 2 mounted on the frame 1; a tilting frame 4 fixedly connected between the two main shafts 3 at their closest ends and driven by the power output end of the tilting motor 2; and a dough mixer drum 5 fixedly mounted on the tilting frame 4. The dough mixer drum 5 includes an inner liner 18 and an outer sheath 15 covering the outer side of the inner liner 18. The outer wall of the inner liner 18 and the inner wall of the outer sheath 15 together form a sealed cooling sandwich chamber; the cooling sandwich chamber is cooled by a refrigerant... The overall flow direction has a refrigerant inlet 6 at the beginning, which connects to the external refrigerant supply, and a refrigerant outlet 7 at the end. Multiple flow guide baffles 17 are spaced apart in the cooling jacket cavity, dividing the cooling jacket cavity into several heat exchange sub-cavities arranged sequentially along the axial direction of the dough mixer cylinder 5. Multiple series connecting components 8 are installed along the axial direction of the outer wall of the outer sheath 15 and span the corresponding flow guide baffles 17 to connect two adjacent heat exchange sub-cavities for refrigerant series flow. The flow ports of two adjacent series connecting components 8 connected to the same heat exchange sub-cavity are staggered in spatial projection.

[0049] In this embodiment, by setting multiple flow guide baffles 17 in the cooling jacket cavity, the originally wide single jacket is cut into multiple independent heat exchange sub-cavities. By using the series connecting components 8 arranged in a spatially staggered manner on the adjacent baffles, the natural flow inertia of the fluid is broken. The cooling medium is forced to flow in a detour and backflow between each sub-cavity, forming a series baffle path. This allows the refrigerant to flush all parts of the outer wall of the inner liner 18, completely eliminating fluid short circuits and stagnant dead zones, and greatly improving the convective heat transfer effect.

[0050] The solution combines the frame 1, the main shaft 3, and the tilting frame 4 driven by the tilting motor 2 to provide an extremely stable cradle-type rotating platform for the heavy-duty dough mixer cylinder 5 carrying a complex cooling jacket. This structure can not only withstand the huge alternating stress during biaxial kneading, but also smoothly achieve a 180° reciprocating tilting unloading action, thus not affecting the unloading.

[0051] During work:

[0052] Under normal dough kneading conditions, the dough kneading machine cylinder 5 is in an upright position supported by the tilting frame 4. The external low-temperature refrigerant is pumped into the first heat exchange sub-chamber from the refrigerant main inlet 6 at the beginning. After the refrigerant fills the sub-chamber and absorbs the heat from the inner liner 18 wall, it can only enter the next heat exchange sub-chamber through the series connection component 8. Since the flow ports of two adjacent series connection components 8 connected to the same heat exchange sub-chamber are staggered in spatial projection, the refrigerant is forced to flow horizontally or vertically in the annular chamber, washing the entire inner liner 18 wall before finding the next outlet. This process is repeated, and the refrigerant flows through all the heat exchange sub-chambers in sequence along the forced change of direction series flow path, and finally carries a large amount of heat out of the system from the refrigerant main outlet 7 at the end.

[0053] When the dough kneading process is finished and unloading is required, the flipping motor 2 starts, and the power is transmitted to the two main shafts 3, which drive the flipping frame 4 and the dough kneading machine cylinder 5 fixed on it to rotate 180° around the axis of the main shaft 3 to an inverted state. The dough is automatically discharged under the action of gravity. In this flipping action and the subsequent return action, the cooling jacket chamber moves synchronously with the cylinder, and the structure is stable.

[0054] Example 2

[0055] like Figure 3 , Figure 4 and Figure 8As shown, based on Embodiment 1, the present invention provides a technical solution: Preferably, a parallel direct supply pipe 11 is axially arranged on the outer wall of the outer sheath 15; the series connection assembly 8 includes: a mounting plate 807; an adjusting cylinder 801, fixed to the side of the mounting plate 807 away from the outer sheath 15 by a reset bracket 806; a valve core 802, axially slidably connected between the inner walls of the adjusting cylinder 801, with two annular grooves 803 spaced apart on the outer circumferential surface of the valve core 802; two series pipes 804, connected to the cylinder wall of the adjusting cylinder 801, the two series pipes 804 respectively connecting to two adjacent heat exchange sub-chambers; along the flow direction of the refrigerant, the two adjacent heat exchange sub-chambers are respectively defined as the upstream heat exchange sub-chamber and the downstream heat exchange sub-chamber; two parallel pipes 805, connected to the cylinder wall of the adjusting cylinder 801. The two parallel pipes 805 are positioned at intervals along the axial direction of the regulating cylinder 801, with the connection positions of the two series pipes 804 on the cylinder wall. One of the parallel pipes 805 is connected to the downstream heat exchange sub-chamber, and the other parallel pipe 805 is connected to the parallel direct supply pipe 11. Both the series pipe 804 and the parallel pipe 805 connected to the downstream heat exchange sub-chamber are equipped with one-way valves. One end of the valve core 802 is fixedly connected to the valve stem 814. A thermal triggering structure is provided on the side of the mounting plate 807 facing the downstream heat exchange sub-chamber. The valve stem 814 passes through the reset frame 806 and the mounting plate 807 and is connected to the thermal triggering structure. The thermal triggering structure is configured such that when an abnormally high temperature is detected in the refrigerant in the downstream heat exchange sub-chamber, the valve stem 814 drives the valve core 802 to move axially.

[0056] The above scheme can effectively eliminate dead zones in the flow of the cooling medium by setting up a series baffle path. However, in actual production, this pure series structure will cause new thermo-hydrodynamic problems: as the cooling channel path is greatly lengthened, the cooling medium will continuously absorb the heat emitted by the dough as it flows through the preceding heat exchange sub-chambers. This will cause the temperature of the cooling medium itself to increase continuously along the path. When the cooling medium has become warm in the path and flows to the heat exchange sub-chamber located in the middle and later part of the path (especially at the intersection of the saddle area in the middle section where the heat generation is the greatest in the twin-shaft dough mixer), the heat transfer temperature difference between it and the inner wall of the inner liner 18 has decreased sharply, and it may even lose its cooling capacity. This heat attenuation phenomenon along the path will cause the temperature of the dough mixer cylinder 5 to increase as it goes further back, and the global temperature distribution of the dough will be severely uneven, which will easily cause the local dough to deform and become sticky due to overheating.

[0057] In this embodiment, by using redundant parallel direct supply pipes 11 in conjunction with the mixed flow control structure, the problem of cooling failure of the end heat exchange sub-chamber caused by the continuous heat absorption of the refrigerant along the flow path in a pure series cooling water circuit is effectively solved. When an abnormally high temperature occurs in a heat exchange sub-chamber due to local intense friction of the dough, the thermal trigger structure can spontaneously sense the change in fluid temperature and drive the valve core 802 to generate axial displacement, thereby changing the alignment state of the annular groove 803 and the pipeline. This linkage mechanism reduces or cuts off the inflow of the series refrigerant carrying heat from upstream, while simultaneously opening the channel of the parallel direct supply pipes 11, so that fresh low-temperature refrigerant that has not undergone prior heat exchange can be directly injected into the overheated heat exchange sub-chamber, thereby quickly and directly suppressing the local temperature rise and ensuring the uniformity and stability of the global temperature distribution of the dough mixer cylinder 5.

[0058] Reference Figure 4 The diagram shows three dashed boxes. The dashed box in the middle represents the refrigerant channel in series under normal conditions, while the dashed box at the bottom shows the refrigerant channel in redundant parallel connection.

[0059] Under normal and surface conditions (no local overheating): the refrigerant temperature in the downstream heat exchange sub-chamber is within the normal range, and the thermal trigger structure on the mounting plate 807 is in an unactivated initial state. At this time, the valve stem 814 does not undergo additional displacement, and the valve core 802 maintains its default position in the regulating cylinder 801. In this default position, the two annular grooves 803 on the valve core 802 are exactly aligned with the two series pipes 804 at the first cross-section position, while being offset from the parallel pipe 805 at the second cross-section position (or maintaining only a very small communication gap). At this time, the refrigerant from the upstream heat exchange sub-chamber flows smoothly into the annular groove 803 of the regulating cylinder 801 through one series pipe 804, and then is discharged into the downstream heat exchange sub-chamber through the other series pipe 804, maintaining the basic series baffle cooling cycle.

[0060] In the case of local overheating triggering: when the dough experiences intense local friction, causing the refrigerant in the downstream heat exchange chamber to reach an abnormally high temperature, the thermal triggering structure senses that the temperature exceeds the threshold, quickly moves, and pushes the valve stem 814 forward. The valve stem 814 causes the valve core 802 to slide axially within the regulating cylinder 801. This sliding instantaneously changes the alignment of the fluid channel: the first annular groove 803 on the valve core 802 gradually deviates from the series pipe 804, causing the flow cross-sectional area of ​​the series pipe 804 to decrease sharply (or even be blocked by the outer wall of the valve core 802), thereby intercepting the ineffective warm water from upstream; at the same time, the second annular groove 803 on the valve core 802 slides and precisely aligns with the two parallel pipes 805 at the second cross-section position, causing the parallel channel to be opened.

[0061] At this time, the low-temperature "fresh" refrigerant in the parallel direct supply pipe 11 passes through the annular groove 803 and flows directly into the downstream heat exchange sub-chamber. The one-way valves installed in the series pipe 804 and the parallel pipe 805 effectively prevent the high-pressure fresh refrigerant from flowing back into the low-pressure upstream chamber or main pipe.

[0062] When the area is cooled by strong cooling, the thermal trigger structure deactivates and retracts. Under the constraint of the reset bracket 806, the valve core 802 slides back to its initial position, cutting off the direct supply of fresh refrigerant and restoring the basic series circulation.

[0063] like Figure 6 , Figure 8 and Figure 9 As shown, in this embodiment, preferably, the thermal triggering structure includes a temperature-sensing housing 811 sealed and fixed to the mounting plate 807 on the side facing the downstream heat exchange sub-chamber. The temperature-sensing housing 811 extends into the interior of the downstream heat exchange sub-chamber to be immersed in the refrigerant. The interior of the temperature-sensing housing 811 is sealed and filled with a thermally sensitive expansion medium 812. An elastic isolation member 813 is fixedly connected inside the temperature-sensing housing 811. One end of the valve stem 814 extends into the unclosed opening of the temperature-sensing housing 811 and is movable. The valve stem 814 is abutted against the elastic isolator 813, which completely seals and encloses the thermosensitive expansion medium 812 inside the temperature sensing housing 811; the elastic isolator 813 separates the thermosensitive expansion medium 812 from the valve stem 814; the valve stem 814 is fixedly connected to the force-bearing boss 815 at the location of the reset frame 806, and a reset spring 816 is sleeved on the outside of the valve stem 814, with the two ends of the reset spring 816 abutting against the inner wall of the reset frame 806 and the force-bearing boss 815 respectively.

[0064] In this embodiment, the huge volume expansion force generated by the thermal phase change of the thermosensitive expansion medium 812 is used as the mechanical driving source. Combined with the force transmission and sealing function of the elastic isolation component 813, it can not only stably output a thrust sufficient to overcome the water pressure of the system, but also eliminate the risk of leakage of the liquid expansion medium. This fully enclosed mechanical structure does not require an external power supply or a complex electronic temperature sensor. In the harsh industrial environment of high dust and high humidity encountered during the operation of the dual-axis dough kneading machine, it has extremely high operational stability, anti-interference ability and extremely low maintenance cost.

[0065] During work:

[0066] The temperature-sensing housing 811 is always immersed in the refrigerant in the downstream heat exchange sub-chamber, and senses the real refrigerant temperature in the area in real time. When the refrigerant temperature is within the normal range, the thermosensitive expansion medium 812 (such as high-purity thermosensitive paraffin with a specific melting point) at the bottom of the temperature-sensing housing 811 is in a solid or contracted state. At this time, the reset spring 816 in the reset frame 806 applies an inward preload force to the valve stem 814 through the force-bearing boss 815, so that the elastic isolation member 813 maintains its initial shape and the valve core 802 is maintained in the basic series flow position.

[0067] When the refrigerant temperature rises abnormally and exceeds the set phase change threshold, the heat penetration and conduction cause the thermosensitive expansion medium 812 to rapidly absorb heat and melt, and undergo violent volume expansion. Since the temperature sensing shell 811 is a rigid constraint, the expanding medium can only violently squeeze the elastic isolation member 813 inward. After being squeezed, the elastic isolation member 813 undergoes elastic protrusion deformation towards the valve stem 814 side. This deformation force directly pushes against one end of the valve stem 814 that is attached to it. When this thrust is greater than the sum of the resistance of the return spring 816 and the water flow resistance, the valve stem 814 extends outward, driving the valve core 802 to complete axial sliding.

[0068] When the chamber is cooled down by a large amount of fresh cold water in parallel, the thermosensitive expansion medium 812 cools down and shrinks back to solid, reducing its volume. The compressive force applied to the elastic isolation member 813 disappears. At this time, the compressed return spring 816 releases its elastic potential energy, pushing the force-bearing boss 815 and valve stem 814 back to their original positions, and the system returns to the normal surface cooling state.

[0069] In a preferred embodiment, the thermosensitive expansion medium 812 is a thermosensitive paraffin doped with thermally conductive metal powder.

[0070] Its specific material properties and working mechanism are as follows: When the temperature-sensitive paraffin is near a specific phase change temperature point (such as the temperature threshold corresponding to the safe heating threshold of the dough), it will undergo a phase change from solid to liquid. This phase change process is accompanied by stable volume expansion, which can generate outward compressive stress inside the rigid temperature-sensitive shell 811. By adjusting the carbon chain length or mixing ratio of the temperature-sensitive paraffin during the preparation process, the target temperature at which the phase change occurs can be accurately determined, thereby adapting to the different requirements of cooling start-up temperature for different dough product processes.

[0071] Because pure paraffin has a low thermal conductivity, it exhibits a certain thermal hysteresis effect. By uniformly doping temperature-sensitive paraffin with high thermal conductivity metal powders such as copper powder and aluminum powder, the overall thermal conductivity of the medium can be significantly improved.

[0072] Example 3

[0073] like Figure 4 , Figure 6 and Figure 11As shown, based on Embodiment 2, the present invention provides a technical solution: preferably, the dough mixer cylinder 5 has an upright dough mixing state and an inverted unloading state after being rotated 180°; each heat exchange sub-chamber is connected to a drain branch pipe 901 at its physical top when it is in the upright dough mixing state, and a buoyancy valve assembly 9 is provided inside the drain branch pipe 901; the buoyancy valve assembly 9 is configured to control the opening and closing of the drain branch pipe 901 according to the rise and fall of the liquid level in the heat exchange sub-chamber when it is in the upright dough mixing state.

[0074] Because the cooling jacket chamber has multiple flow guide baffles 17, the flow channel structure is relatively complex. During the initial water injection or normal operation of the system, the gas released from the fluid tends to accumulate at the top of each heat exchange sub-chamber. The accumulated gas will form gas resistance, which not only reduces the convective heat transfer area in this area, but also interferes with the intended flow path of the refrigerant. If a normally open vent is opened at the top of the cylinder, it will cause continuous refrigerant leakage during operation; if a conventional manual vent valve is used, it cannot meet the automated operation requirements of industrial equipment.

[0075] In this embodiment, by setting a buoyancy valve assembly 9 controlled by liquid level at the physical top of each heat exchange sub-chamber when it is in the upright state, the passive automatic venting function of the system is realized. It can use the buoyancy of the fluid itself and the liquid level change as the driving source. When gas accumulates, it automatically opens the venting path and automatically resets the seal after the gas is exhausted. This ensures that the heat exchange sub-chamber is always filled with refrigerant, maintains the expected heat exchange area, and does not require manual intervention or the introduction of additional electrical control nodes. It meets the fluid pressure holding and anti-gas lock requirements of the dough mixer in the upright working state.

[0076] When the dough mixer cylinder 5 is in the upright dough mixing state, the fluid enters the heat exchange sub-chamber. If there is gas in the chamber, the gas will rise naturally due to buoyancy and accumulate at the physical top of the heat exchange sub-chamber (i.e., the part where the drain branch pipe 901 connects to the heat exchange sub-chamber). This causes the refrigerant level in this local area to drop relatively. The buoyancy valve assembly 9 inside the drain branch pipe 901 will act as the liquid level drops, thereby opening the drain branch pipe 901 to discharge the accumulated gas.

[0077] As the gas is gradually discharged, the refrigerant level rises and fills the top of the heat exchange chamber. The buoyancy valve assembly 9 is completely submerged in the refrigerant and is displaced by the upward buoyancy of the refrigerant, thereby blocking the channel of the drain branch pipe 901. In the subsequent normal kneading process, the buoyancy valve assembly 9 cycles the above actions according to the change of the gas-liquid ratio in the chamber, realizing continuous automatic venting and closed-loop sealing.

[0078] Example 4

[0079] like Figure 10 , Figure 11 and Figure 12As shown, based on Embodiment 3, the present invention provides a technical solution: Preferably, a return water main pipe 10 communicating with an external refrigerant recovery end is axially arranged on the outer wall of the outer sheath 15; each drain branch pipe 901 is connected to the return water main pipe 10; the buoyancy valve assembly 9 includes an end cap 911 fixedly connected to one end of the drain branch pipe 901, an end seat 902 fixedly connected inside the end cap 911, a linkage rod 903 inserted through the middle of the end seat 902, a plug 904 fixedly connected to one end of the linkage rod 903, and a float 905 fixedly connected to the other end of the linkage rod 903, which extends into the interior of the heat exchange sub-chamber. The inner wall of the drain branch pipe 901 has a protrusion forming a sealing part 910. The end face of the plug 904 facing the sealing part 910 has a conical sealing slope. The conical sealing slope abuts against the sealing part 910 to form an end face seal. The drain branch pipe 901 is fixedly connected to a ring seat 908. The middle of the ring seat 908 is slidably connected to a guide rod 906. One end of the guide rod 906 is fixedly connected to the plug 904, and the other end is fixedly connected to a limit head 909. A control spring 907 is sleeved on the outside of the guide rod 906. The two ends of the control spring 907 abut against the plug 904 and the ring seat 908 respectively.

[0080] In actual production, the twin-shaft rotary dough mixer operates cyclically, typically consisting of two main stages: upright dough mixing and inverted unloading. During the inverted unloading stage, the high shear friction heat generation of the dough ceases, significantly reducing the system's cooling requirements. However, the external industrial chiller and circulating water pump supplying refrigerant to large dough mixers should not be frequently started and stopped, otherwise, it will severely affect the service life of core components such as the compressor. If the original refrigerant circulation is maintained during the inverted unloading period, the refrigerant still needs to flow through a complex series of baffles 17, causing the circulating water pump to continuously bear high back pressure in the pipeline system under conditions without effective heat load, resulting in unnecessary pumping energy loss.

[0081] In this embodiment, the adaptive action of the dual-guide buoyancy valve assembly 9 under different equipment postures effectively solves the problem of high back pressure and energy consumption in the pipeline network during the unloading idle period of the continuous cooling system. When the dough mixer cylinder 5 flips to the inverted unloading state, the drain branch pipe 901 is inverted at the bottom. The direction of the refrigerant buoyancy force on the float 905 and the direction of the elastic force of the control spring 907 are superimposed in the same direction in the valve body axis, jointly driving the plug 904 to disengage from the sealing part 910. When the equipment is inverted, the drain channels between each heat exchange sub-chamber and the return water main pipe 10 are passively and forcibly opened, instantly switching the originally series high-resistance pipeline network to multiple parallel low-resistance bypass pipelines. This design allows the external chiller and water pump to maintain basic refrigerant flow with extremely low system back pressure without shutting down or interrupting the circulation. This avoids frequent start-ups and shutdowns of the refrigeration equipment, effectively reduces the standby energy consumption of the water pump, and removes residual heat from the cylinder metal through continuous low-resistance circulation. It also keeps the cooling jacket fully filled with refrigerant, ensuring that the equipment can seamlessly transition to high-intensity cooling mode when returning to center for the next batch of dough kneading operations.

[0082] Reference Figure 4 The dotted box at the top is the area where the drain branch pipe 901 and the return water main pipe 10 are located. When the dough mixer cylinder 5 is in the upright dough mixing state, the drain branch pipe 901 is located at the physical top of the heat exchange sub-chamber. As the refrigerant fills the heat exchange sub-chamber, the float 905 is completely submerged and generates upward buoyancy. When this buoyancy is greater than the sum of the initial preload applied by the control spring 907 and the weight of the component, the float 905 drives the plug 904 to move upward through the linkage rod 903 and tightly abut against the sealing part 910 on the inner wall of the drain branch pipe 901, completing the physical sealing of the bypass branch. This forces the refrigerant to overcome the pipeline resistance and flow sequentially along the predetermined series baffle path for efficient heat exchange.

[0083] When the dough mixing process is completed, the dough mixer cylinder 5 rotates 180° to the inverted unloading position, and the drain branch pipe 901 rotates to the bottom of the heat exchange sub-chamber. At this time, the refrigerant gathers at the bottom under the influence of gravity and submerges the float 905. The float 905 is subjected to an upward buoyancy force. Due to the inverted position of the equipment, the direction of this buoyancy force is the same as the direction of the elastic force of the control spring 907 pushing the plug 904 away from the sealing part 910. Under the superposition of the buoyancy force and the spring force in the same direction, the plug 904 is quickly pushed away from the sealing part 910, and the drain branch pipe 901 is in a fully open conductive state. At this time, the refrigerant entering the cooling jacket chamber no longer passes through the high-resistance guide pipe sequentially. Instead of flowing through the baffle 17, the liquid flows directly into the parallel return main pipe 10 through the large-area open drain branches 901. The overall water resistance of the system network drops sharply, and the output pressure of the external circulating water pump is greatly reduced while maintaining the same flow rate. When the unloading is completed and the equipment returns to the upright position, the force direction of the plug 904 is reversed, and the buoyancy valve assembly 9 is driven by the rise of the refrigerant level to overcome the control spring 907 and close. The system automatically returns to the high-resistance series cooling path.

[0084] like Figure 2 , Figure 5 and Figure 13 As shown, in this embodiment, preferably, the refrigerant main inlet 6 is connected to the parallel direct supply pipe 11; the refrigerant main outlet 7 is connected to the return water main pipe 10; both main shafts 3 have axially extending hollow flow channels 301 inside, and radial through holes 302 communicating with the hollow flow channels 301 are opened on the outer wall of the main shafts 3; both main shafts 3 have sleeve-type rotary joints 12 fitted on their outer walls, each sleeve-type rotary joint 12 including a stationary stator outer ring 121, and an annular liquid collection cavity is formed between the inner wall of the stator outer ring 121 and the outer wall of the main shaft 3. 122, the annular liquid collection chamber 122 remains in communication with the radial through hole 302 during the rotation of the main shaft 3; the hollow flow channel 301 inside the main shaft 3 located on one side is connected to the return water main pipe 10, and the stator outer ring 121 sleeved on the main shaft 3 on this side is provided with an external port 123 for connecting to the external refrigerant recovery end; the hollow flow channel 301 inside the main shaft 3 located on the other side is connected to the parallel direct supply pipe 11, and the stator outer ring 121 sleeved on the main shaft 3 on this side is provided with an external port 123 for connecting to the external refrigerant supply end.

[0085] Specifically, the stator outer ring 121 (fixedly connected to the frame 1) remains stationary to connect to external pipelines. To ensure smooth rotation of the main shaft 3 and fluid tightness, a rotational assembly gap is provided between the inner wall of the stator outer ring 121 and the outer wall of the main shaft 3. Rotary dynamic sealing assemblies (such as mechanical seal rings, lip seals, or wear-resistant seals commonly used in mature rotary joint technology) are symmetrically arranged at both axial ends of the annular liquid collection cavity 122 between the stator outer ring 121 and the main shaft 3, and are supplemented by bearings for coaxial guiding support. When the main shaft 3 rotates 180° reciprocatingly, the rotary dynamic sealing assemblies on both sides dynamically fill the rotational gap, ensuring that the annular liquid collection cavity 122 always remains a liquid-tight, closed, high-pressure annular space. Therefore, the refrigerant can achieve a stable transition between the stationary external port 123 and the rotating radial through-hole 302 without external leakage.

[0086] When the dough mixer cylinder 5 with cooling jacket is unloading, it needs to rotate 180° around the axis of the main shaft 3 along with the jacket. If a flexible hose is directly used to connect the external fixed refrigerant supply pipeline to the movable cylinder jacket, the hose is very prone to entanglement, excessive stretching and bending fatigue during the frequent large-angle reversal of the equipment, which will lead to pipeline rupture and refrigerant leakage.

[0087] In this embodiment, by installing a sleeve-type rotary joint 12 on the outer wall of the main shaft 3 and cooperating with the hollow flow channel 301 inside the main shaft 3, a rigid fluid transition channel between the external stationary pipeline and the moving cylinder is constructed while avoiding the mechanical transmission and support space at the end of the main shaft 3. The stator outer ring 121 remains stationary to connect with the external pipeline, and its internal annular liquid collecting cavity 122 covers the outer wall of the main shaft 3, so that when the main shaft 3 rotates 180°, the radial through hole 302 always remains in communication with the liquid cavity, completely eliminating the risk of entanglement and fatigue fracture of the flexible hose caused by equipment rotation.

[0088] Meanwhile, one side of the main shaft 3 is defined as a pure liquid inlet channel (connecting the parallel direct supply pipe 11 and the first end chamber), and the other side of the main shaft 3 is defined as a pure liquid outlet channel (connecting the return water main pipe 10 and the tail end chamber), which establishes a clear topological direction of the fluid inside the system and avoids disordered mixing or short circuit of the hot and cold media in the main supply pipeline.

[0089] The refrigerant main inlet 6, refrigerant main outlet 7, return water main pipe 10, and parallel direct supply pipe 11 are all used as follow-up pipes, which are fixedly installed on the outer sheath 15 of the dough mixer cylinder 5 and rotate synchronously with the dough mixer cylinder 5 and the main shaft 3. Since the main shaft 3 and the dough mixer cylinder 5 are relatively stationary (the two rotate synchronously), the inner end of the main shaft 3 is rigidly sealed to the above-mentioned follow-up pipes.

[0090] On the refrigerant supply side (liquid inlet side), Figure 2 (On the side furthest from the flip motor 2): External static refrigerant enters the external port 123 on the stator outer ring 121 on this side, fills the annular liquid collection chamber 122, and then enters the hollow flow channel 301 inside the main shaft 3 on this side through the radial through hole 302. The high-pressure fresh refrigerant flowing out of the hollow flow channel 301 first enters the starting end of the parallel direct supply pipe 11, and then is physically diverted through a four-way pipe joint: two of the pipes are rigidly connected to the two refrigerant inlets 6 on both sides, injecting the refrigerant into the heat exchange sub-chamber at the very beginning of the cooling jacket chamber, as the source of series baffle cooling; the other of the four-way pipe joint is connected to the extension pipe of the parallel direct supply pipe 11, so that the refrigerant is retained here as the backup refrigerant required by each group of thermosensitive mixing control structures;

[0091] On the refrigerant recovery side (drainage side), Figure 2 On the side closer to the flip motor 2: the refrigerant discharged from each buoyancy valve assembly 9 is collected in two return water mains 10 on both sides. The ends of these two return water mains 10 are first connected to a return water extension pipe through a tee pipe joint. Figure 3 The return water is located in the vertical pipe between the main refrigerant outlet 7 and the return water main pipe 10. Then, the return water extension pipe merges with the two main refrigerant outlets 7 discharged from the tail end of the cooling jacket. The three are connected and merged through a four-way pipe joint. The merged return water is rigidly connected to the hollow flow channel 301 inside the drain side main shaft 3 through the transition short pipe. The collected return water flows outward along the hollow flow channel 301 and is thrown into the annular liquid collection chamber 122 of the sleeve-type rotary joint 12 on this side through the radial through hole 302. Finally, it is discharged into the external refrigerant recovery end through the external port 123 on the stator outer ring 121.

[0092] like Figure 6 As shown, preferably, the outer surface of the outer sheath 15 is fully covered with a cryogenic insulation layer 16, and a protective shell 19 for protecting the appearance of the equipment is provided on the outside of the cryogenic insulation layer 16; the protective shell 19 and the outer sheath 15 are connected and supported by a plurality of non-metallic heat-insulating support blocks spaced apart.

[0093] The dough mixing workshop usually has high air humidity. Heat in the workshop environment will be conducted to the cooling jacket in large quantities through the metal connection nodes, resulting in the loss of cooling medium. At the same time, the local temperature on the surface of the outer sheath 15 will cause water vapor in the air to condense on the surface of the equipment shell.

[0094] In this embodiment, by setting a non-metallic thermal insulation support block between the outer sheath 15 and the protective shell 19, the solid heat conduction path between the inner and outer metal structures is effectively cut off, constructing a physically broken bridge thermal insulation system. Combined with the full coverage of the cryogenic insulation layer 16, this structure, while ensuring the mechanical support strength of the protective shell 19, completely thermally isolates the cooling interlayer chamber from the external environment, significantly reducing the unnecessary energy consumption of the refrigeration system to the environment, and enabling the overall surface temperature of the protective shell 19 to be stably maintained above the environmental dew point. This eliminates the phenomenon of condensation and dripping water on the outer surface of the equipment from the root, and meets the clean production requirements of high-humidity food processing environments.

[0095] like Figure 3 and Figure 6 As shown, preferably, two stirring shafts are arranged parallel to each other and rotatably inside the inner liner 18; the bottom cross-section of the inner liner 18 has a W-shaped structure adapted to the two stirring shafts, and the bottom center of the W-shaped structure has an upwardly protruding saddle-shaped part corresponding to the high shear zone where the two stirring shafts intersect. Figure 6 The bottom of the outer sheath 15 and the bottom edge contour of the multiple flow guide baffles 17 are all contoured and undulating to match the W-shaped structure.

[0096] The inner liner 18 of the dual-shaft rotary drum dough mixer has a structure different from that of a conventional cylindrical reactor. In order to accommodate the rotation trajectory of the two parallel stirring shafts, its bottom inevitably presents a "W"-shaped double-arc intersecting cross section. This special structure forms an upward-protruding saddle at the center of the bottom of the inner liner 18. During the dough mixing process, the two stirring shafts converge above this saddle, applying extremely strong shearing, stretching, and squeezing forces to the dough. Therefore, this saddle area is the core hot spot where frictional heat generation is most concentrated and the temperature rise is most intense within the entire dough mixer cylinder 5. If a conventional cylindrical cooling outer jacket 15 is used, the cooling medium inside the jacket will be far away from this core hot spot, or a wide, slow-flowing dead zone will be formed in this area, which will not be able to remove the huge amount of heat.

[0097] In this embodiment, by designing the bottom of the outer sheath 15 and the bottom edge contour of the multiple flow guide baffles 17 as a contoured undulating structure consistent with the "W"-shaped structure of the inner liner 18, a constant cross-section cooling channel that closely adheres to the outer wall of the saddle section is constructed. In actual operation, this contoured structure acts like a mold, forcing the cooling medium to climb up the slope along the saddle section and cross the protruding area when flowing through the bottom of the heat exchange chamber, thereby enabling high-velocity forced convection flushing and heat exchange in the core high-heat area, thoroughly eliminating the heat accumulation below the saddle section and ensuring the stability of the temperature in the high-shear zone of the dough.

[0098] like Figure 1 , Figure 2 and Figure 6As shown, preferably, the two main shafts 3 are coaxially fixedly fitted with load-bearing support plates 14 on their outer sides; auxiliary support components that cooperate with the load-bearing support plates 14 are provided on the bottom of both sides of the frame 1 to share the radial heavy load when the dough mixer cylinder 5 is fully loaded and overturned; each auxiliary support component includes a set of two parallel auxiliary support wheels 13, which are symmetrically distributed and rotatably connected to the frame 1.

[0099] The industrial-grade twin-shaft dough mixer has an extremely large total weight when fully loaded with dough. Since the equipment needs to rotate 180° around the main shaft 3 to unload the dough, if the weight of the entire cylinder and the huge off-center impact force generated during the kneading process are all borne by the cantilever bearing at the end of the main shaft 3, it is very easy for the main shaft 3 to bend and deform.

[0100] In this embodiment, by adding a load-bearing support plate 14 to the outside of the main shaft 3 and configuring an auxiliary support assembly consisting of two parallel auxiliary support wheels 13 at the bottom of the frame 1, a cradle-type lifting structure similar to a heavy-duty rotary kiln is constructed. This not only significantly reduces the radial stress borne by the end of the main shaft 3, ensuring the absolute straightness and joint sealing of the main shaft 3 during rotation, but also provides extremely high mechanical stability for the 180° reciprocating rotation of the equipment, avoiding left and right swaying of the equipment during rotation and high-load kneading.

[0101] The present invention has been described in detail above. However, modifications or improvements can be made to it, which will be obvious to those skilled in the art. Therefore, any modifications or improvements that do not depart from the spirit of the present invention are within the scope of protection of the present invention.

Claims

1. A dual-axis rotary drum and dough sheeter cooling device, comprising a frame (1), wherein two main shafts (3) are symmetrically rotatably connected to the inner side of the frame (1); characterized in that, Also includes: A flip motor (2) is installed on the frame (1); The tilting frame (4) is fixedly connected between the two main shafts (3) at their close ends and is connected to the power output end of the tilting motor (2) via transmission. The dough mixer cylinder (5) is fixedly installed on the flipping frame (4). The dough mixer cylinder (5) includes an inner liner (18) and an outer sheath (15) covering the outside of the inner liner (18). The outer wall of the inner liner (18) and the inner wall of the outer sheath (15) form a closed cooling interlayer chamber. The cooling interlayer chamber has a total refrigerant inlet (6) at the beginning of the refrigerant flow direction and a total refrigerant outlet (7) at the end. A plurality of flow guide baffles (17) are provided at intervals in the cooling jacket cavity. The flow guide baffles (17) divide the cooling jacket cavity into a plurality of heat exchange sub-cavities arranged sequentially along the axial direction of the dough mixer cylinder (5). Multiple series-connecting components (8) are installed axially along the outer wall of the outer sheath (15) and span the corresponding flow guide baffles (17) to connect two adjacent heat exchange sub-chambers for refrigerant to flow in series; the flow ports of two adjacent series-connecting components (8) connected to the same heat exchange sub-chamber are staggered in spatial projection. Parallel direct supply pipes (11) are provided along the axial direction on the outer wall of the outer sheath (15). The series connection assembly (8) includes: a mounting plate (807); an adjusting cylinder (801), fixed to the side of the mounting plate (807) away from the outer sheath (15) by a reset bracket (806); a valve core (802), slidably connected axially to the inner wall of the adjusting cylinder (801), with two annular grooves (803) spaced apart on the outer circumferential surface of the valve core (802); two series pipes (804), connected to the cylinder wall of the adjusting cylinder (801), the two series pipes (804) respectively connected to two adjacent heat exchange sub-chambers; along the flow direction of the refrigerant, the two adjacent heat exchange sub-chambers are respectively defined as the upstream heat exchange sub-chamber and the downstream heat exchange sub-chamber; and two parallel pipes (805), connected to the cylinder wall of the adjusting cylinder (801), and the two parallel pipes... The connection positions of the connecting pipe (805) on the wall of the regulating cylinder (801) and the connection positions of the two series pipes (804) are distributed at intervals along the axial direction of the regulating cylinder (801). One of the parallel pipes (805) is connected to the downstream heat exchange sub-chamber, and the other parallel pipe (805) is connected to the parallel direct supply pipe (11). One-way valves are provided in both the series pipe (804) and the parallel pipe (805) connected to the downstream heat exchange sub-chamber. A valve stem (814) is fixedly connected to one end of the valve core (802). A thermal triggering structure is provided on the side of the mounting plate (807) facing the downstream heat exchange sub-chamber. The valve stem (814) passes through the reset frame (806) and the mounting plate (807) and is drivenly connected to the thermal triggering structure. The thermal triggering structure is configured such that when an abnormally high temperature is detected in the refrigerant in the downstream heat exchange sub-chamber, the valve stem (814) is driven to cause the valve core (802) to undergo axial displacement.

2. The dual-axis rotary drum and dough sheeter cooling device according to claim 1, characterized in that: The thermal triggering structure includes a temperature-sensing housing (811) sealed and fixed to the mounting plate (807) on the side facing the downstream heat exchange sub-chamber. The temperature-sensing housing (811) extends into the interior of the downstream heat exchange sub-chamber to be immersed in the refrigerant. The interior of the temperature-sensing housing (811) is sealed and filled with a thermal expansion medium (812). An elastic isolator (813) is fixedly connected to the interior of the temperature-sensing housing (811). One end of the valve stem (814) extends into the unclosed opening of the temperature-sensing housing (811) and movably abuts against the elastic isolator (813). The elastic isolator (813) completely seals and encloses the thermosensitive expansion medium (812) inside the temperature sensing housing (811); the elastic isolator (813) separates the thermosensitive expansion medium (812) from the valve stem (814); the valve stem (814) is fixedly connected to the force-bearing boss (815) at the location of the reset frame (806), and a reset spring (816) is sleeved on the outside of the valve stem (814), with the two ends of the reset spring (816) respectively abutting between the inner wall of the reset frame (806) and the force-bearing boss (815).

3. The dual-axis rotary drum and dough sheeter cooling device according to claim 2, characterized in that: The dough mixer cylinder (5) has an upright dough mixing state and an inverted unloading state after being flipped 180°; each heat exchange sub-chamber is connected to a drain branch pipe (901) at its physical top when it is in the upright dough mixing state, and a buoyancy valve assembly (9) is provided inside the drain branch pipe (901); the buoyancy valve assembly (9) is configured to control the opening and closing of the drain branch pipe (901) according to the rise and fall of the liquid level in the heat exchange sub-chamber when it is in the upright dough mixing state.

4. The dual-axis rotary drum and dough sheeter cooling device according to claim 3, characterized in that: The outer wall of the outer sheath (15) is provided with a return water main pipe (10) connected to the external refrigerant recovery end along the axial direction; each of the drain branch pipes (901) is connected to the return water main pipe (10); the buoyancy valve assembly (9) includes an end cap (911) fixedly connected to one end of the drain branch pipe (901), an end seat (902) fixedly connected inside the end cap (911), a linkage rod (903) is inserted through the middle of the end seat (902), a plug (904) is fixedly connected to one end of the linkage rod (903), and the other end extends into the interior of the heat exchange sub-chamber and is fixedly connected to a float (905); the inner wall of the drain branch pipe (901) has a protrusion forming a seal. The plug (904) of the part (910) has a tapered sealing slope on one end face facing the sealing part (910). The tapered sealing slope abuts against the sealing part (910) to form an end face seal. The drain branch pipe (901) is fixedly connected to a ring seat (908). A guide rod (906) is slidably connected to the middle of the ring seat (908). One end of the guide rod (906) is fixedly connected to the plug (904), and the other end is fixedly connected to a limit head (909). A control spring (907) is sleeved on the outside of the guide rod (906). The two ends of the control spring (907) abut against the plug (904) and the ring seat (908) respectively.

5. A dual-axis rotary drum and dough sheeter cooling device according to claim 4, characterized in that: The refrigerant inlet (6) is connected to the parallel direct supply pipe (11); the refrigerant outlet (7) is connected to the return water main pipe (10); both main shafts (3) have axially extending hollow flow channels (301) inside, and the outer wall of the main shaft (3) has radial through holes (302) connecting the hollow flow channels (301); both main shafts (3) have sleeve-type rotary joints (12) fitted on their outer walls, the sleeve-type rotary joints (12) including a stationary stator outer ring (121), the inner wall of the stator outer ring (121) and the outer wall of the main shaft (3) enclose an annular liquid collection cavity (122) formed between them. The annular liquid collection chamber (122) is always connected to the radial through hole (302) during the rotation of the main shaft (3); the hollow flow channel (301) inside the main shaft (3) located on one side is connected to the return water main pipe (10), and the stator outer ring (121) sleeved on the main shaft (3) on this side is provided with an external port (123) for connecting to the external refrigerant recovery end; the hollow flow channel (301) inside the main shaft (3) located on the other side is connected to the parallel direct supply pipe (11), and the stator outer ring (121) sleeved on the main shaft (3) on this side is provided with an external port (123) for connecting to the external refrigerant supply end.

6. The dual-axis rotary drum and dough sheeter cooling device according to claim 5, characterized in that: The outer surface of the outer sheath (15) is fully covered with a cryogenic insulation layer (16), and a protective shell (19) for protecting the appearance of the equipment is provided on the outside of the cryogenic insulation layer (16); the protective shell (19) and the outer sheath (15) are connected and supported by multiple non-metallic heat-insulating support blocks distributed at intervals.

7. A dual-axis rotary drum and dough sheeter cooling device according to claim 6, characterized in that: The inner liner (18) has two parallel and rotatable stirring shafts inside; the bottom cross section of the inner liner (18) is a W-shaped structure adapted to the two stirring shafts, and the bottom center of the W-shaped structure has an upwardly protruding saddle part corresponding to the high shear zone where the two stirring shafts intersect; the bottom of the outer sheath (15) and the bottom edge contour of the multiple flow guide baffles (17) are all in a contoured undulating structure adapted to the W-shaped structure.

8. A dual-axis rotary drum and dough sheeter cooling device according to claim 7, characterized in that: The two main shafts (3) are coaxially fixedly fitted with load-bearing support plates (14); the bottom of both sides of the frame (1) are provided with auxiliary support components that cooperate with the load-bearing support plates (14) to share the radial heavy load when the dough mixer cylinder (5) is fully loaded and overturned; each auxiliary support component includes a set of two parallel auxiliary support wheels (13), the two auxiliary support wheels (13) are symmetrically distributed and rotatably connected to the frame (1).

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