Self-adjusting oil pump system, compressor and refrigeration equipment

Abstract

The invention provides a self-adjusting oil pump system, a compressor and refrigeration equipment. The self-adjusting oil pump system comprises a crankshaft and a self-adjusting oil pump assembly. The self-adjusting oil pump assembly comprises a sliding valve, a thermal induction part and an oil guiding part which are sequentially arranged in the axial direction of the long shaft. After being heated, the thermal induction part can deform and drive the sliding valve to move from the first working position to the second working position in the axial direction of the main oil duct; at the first working position, the first-stage oil inlet is communicated with the main oil hole through the second oil distributing hole, and the first oil distributing hole is not communicated with the first-stage oil inlet; and at the second working position, the first-stage oil inlet is communicated with the main oil hole through the first branch oil hole. The self-adjusting oil pump system solves the problems that in the prior art, unbalanced inertia force can be generated in the rotating process, so that operation power consumption of a compressor is increased, and noise is intensified; and the problem that when an existing compressor operates under the high-frequency working condition or the high-pressure-difference working condition, due to the fact that the oil pumping amount is insufficient, parts are abraded and leaked is solved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and more specifically, to a self-regulating oil pump system, a compressor, and a refrigeration device. Background Art

[0002] For a reciprocating piston compressor, the suction and discharge valve assemblies, the cylinders on the cylinder block, and the pistons that can perform linear reciprocating motion form a closed compression chamber. The cylinder head completely covers the suction and discharge valve assemblies to form a closed discharge chamber. When the piston performs linear reciprocating motion in the cylinder, the refrigerant gas in the compressor housing can be inhaled, then the refrigerant gas is compressed and worked on, and then the compressed refrigerant gas is discharged into the discharge chamber, thus forming a cycle of suction, compression, and discharge. Finally, the high-pressure refrigerant gas in the discharge chamber is transported to the outside of the compressor through the internal discharge coil and enters the refrigeration cycle system such as a refrigerator.

[0003] When the refrigerator needs to quickly reach the instant freezing effect of -35°C, it is required that the piston compressor operates at a high frequency above 100 Hz. As the operating frequency of the compressor increases rapidly, higher requirements are also put forward for the oil lubrication between the compressor components, that is, more lubricating oil is required between the components under high-frequency conditions to form a stable oil film to avoid wear between the components. Therefore, the oil pumping capacity of the compressor is increased under high-frequency conditions. To increase the oil pumping capacity, generally a spiral oil pumping structure is added at the lower end of the crankshaft of the piston compressor. For example, there is an existing oil pumping device applicable to a wide range of rotational speeds of the compressor. Although this spiral oil pumping structure can increase the oil pumping capacity of the compressor under high-frequency conditions, it also increases the oil pumping capacity under medium- and low-frequency conditions, that is, it cannot adjust the oil pumping capacity according to the different operating frequencies of the compressor. When the refrigerator door is closed, the compressor will operate for a long time under a low-frequency condition below 33 Hz. Under the low-frequency condition, in addition to lubricating the components, the excessive lubricating oil on the spiral oil pump will also form an oil mist and form a mixed oil-gas mixture with the refrigerant gas. That is, under the low-frequency condition, the more the oil pumping capacity of the spiral oil pumping structure, the greater the proportion of lubrication in the oil-gas mixture inhaled into the compression chamber, and the smaller the proportion of the refrigerant gas, which will eventually lead to a decrease in the volumetric efficiency of the compression chamber under the low-frequency condition and ultimately a decrease in the refrigerating capacity of the compressor under the low-frequency condition.

[0004] In consideration of being able to simultaneously meet the requirement of reducing the oil pumping capacity of the compressor under low-frequency conditions and increasing the oil pumping capacity of the compressor under high-frequency conditions, there are currently three variable oil volume adjustment technologies for small piston compressors.

[0005] The first type is to add an unbalanced plug block connected by a spring in the main oil passage of the crankshaft. This unbalanced plug block will block the oil distribution hole connecting the spiral oil distribution passage as the rotational speed of the crankshaft increases, that is, it realizes the opening and closing function of the plug block on the oil distribution hole of the crankshaft through the high-speed centrifugal force of the crankshaft. However, when the pressure difference between the suction and discharge pressures of the compressor is above 1.5 MPa and the compressor is operating under high-frequency and high-speed conditions, the temperature inside the compressor can reach above 100 °C, which further leads to a greater decrease in the viscosity of the lubricating oil. At this time, the oil pumping volume is small, and a stable lubricating oil film cannot be formed between the compressor components to prevent the components from being worn. At this time, this self-regulating structure has been closed and cannot provide more lubricating oil to the pump body parts to improve the lubrication and oil film sealing between the components, and there is a risk of component wear. Moreover, the sealing effect formed by the oil film between the piston and the cylinder will also be weakened, leakage will increase, and the refrigeration performance of the compressor will also decrease accordingly. At the same time, since there is also an oil distribution passage at the upper end in the axial direction of the main oil passage of the crankshaft, the upper end of the spring of this self-regulating oil pump structure is not restricted. During the high-speed rotation of the crankshaft, the plug block connected by the spring may directly move upward and does not block the oil distribution hole connecting the spiral oil distribution passage of the crankshaft, that is, this self-regulating oil pump structure fails to play the role of opening or closing.

[0006] The second type of self-regulating oil pump structure is a combined structure of a valve plate and a counterweight. The counterweight is arranged on the periphery of the valve plate. As the rotational speed increases, the counterweight drives the valve plate to open under the action of centrifugal force, thereby increasing the oil pumping volume, that is, the oil film lubrication and sealing between the components under high-frequency operating conditions of the compressor are ensured. However, when the pressure difference between the suction and discharge pressures of the compressor is above 1.5 MPa and the compressor is operating at a low speed under medium- and low-frequency conditions, the self-regulating oil pump structure that adjusts the switch through the rotational speed does not start working, that is, the valve plate controlling the oil flow is still in a closed state. At this time, the temperature inside the compressor is also relatively high, which further leads to a decrease in the viscosity of the lubricating oil inside the compressor. At this time, the oil pumping volume is small, and thus a stable lubricating oil film cannot be formed between the components to prevent the problem of component wear. At the same time, this self-regulating oil pump structure is more complex, uses more components, and its reliability cannot be guaranteed.

[0007] The third type is that an oil inlet is provided at the bottom of the liftable sliding valve. An oil ring matching the oil distribution channel communicated with the spiral oil distribution channel is arranged on the outer ring at the top of the sliding valve. Oil holes communicated with the inner cavity of the sliding valve are opened on the oil ring. The lifting height of the sliding valve is less than the sum of the diameter of the oil distribution channel communicated with the spiral oil channel and the diameter of the oil hole communicated with the inner cavity of the sliding valve. A guide oil pipe with a spiral oil pump is also assembled at the bottom of the sliding valve to increase the oil pumping volume. At low rotational speeds, the oil pumping volume is small, and the sliding valve is partially lifted, so that a throttling state exists between the oil distribution channel communicating the main oil channel with the spiral oil distribution channel and the oil ring of the sliding valve. As the rotational speed of the crankshaft increases, the oil pumping volume increases, and the sliding valve is lifted, so that a fully communicated state exists between the oil distribution channel communicating the main oil channel with the spiral oil distribution channel and the oil ring. However, when the pressure difference between the suction and discharge pressures of the compressor is above 1.5 MPa and the compressor is operating at a low speed under medium- and low-frequency working conditions, the self-regulating oil pump structure is controlled to be in a throttling state by the rotational speed. However, at this time, the temperature inside the compressor is relatively high, which in turn causes the viscosity of the lubricating oil inside the compressor to decrease. However, the oil pumping volume at this time is small, so that a stable lubricating oil film cannot be formed between the components to avoid the problem of component wear.

[0008] Moreover, both the first type and the second type use centrifugal force to enable the unbalanced structure to achieve the functions of opening and closing. However, this unbalanced block will increase the redundant unbalanced inertia force, thereby increasing the power loss caused by the unbalanced force. Moreover, it also causes an increase in the frictional force between the compressor crankshaft and the cylinder block, an increase in the frictional power consumption, an increase in the vibration of the compressor, and an increase in the noise, affecting the user experience. An additional balancing structure needs to be added to balance this unbalanced inertia force, but this will also make the structure of the compressor more complex and the reliability more difficult to guarantee. Summary of the Invention

[0009] The first object of the present invention is to provide a self-regulating oil pump system, which solves the problems that the existing self-regulating oil pump structure will generate unbalanced inertia force during rotation, resulting in an increase in the operating power consumption of the compressor, an increase in vibration and noise, and at the same time solves the problems of component wear and leakage caused by insufficient oil pumping volume when the existing broadband piston compressor operates under high-frequency working conditions or high-pressure difference working conditions.

[0010] The second object of the present invention is to provide a compressor adopting the above self-regulating oil pump system.

[0011] The third object of the present invention is to provide a refrigeration device adopting the above compressor.

[0012] To achieve the above first object, the present invention provides a self-regulating oil pump system, including a crankshaft; the crankshaft includes a long shaft, a crank and a short shaft connected in sequence, and a primary oil supply passage and a secondary oil supply passage are provided on the crankshaft. A main oil passage is provided at one end of the long shaft away from the short shaft. The primary oil supply passage has a primary oil inlet and a primary oil outlet, and the secondary oil supply passage has a secondary oil inlet and a secondary oil outlet. The primary oil inlet and the secondary oil inlet are both communicated with the main oil passage. The primary oil outlet is located on the short shaft, and the secondary oil outlet is located on the end wall of the crank facing the short shaft; the self-regulating oil pump system further includes a self-regulating oil pump assembly installed in the main oil passage; the self-regulating oil pump assembly includes a sliding valve, a thermal sensing component and an oil guiding component arranged in sequence along the axial direction of the long shaft; the first end of the thermal sensing component is fixed relative to the long shaft, and the second end of the thermal sensing component is connected to the sliding valve; the sliding valve is provided with a main oil hole, a first oil distribution hole and a second oil distribution hole. Both the first oil distribution hole and the second oil distribution hole are communicated with the main oil passage through the main oil hole. The second oil distribution hole is located on the end wall of the sliding valve away from the thermal sensing component, and the secondary oil supply passage is communicated with the main oil hole through the second oil distribution hole. The first oil distribution hole is located on the peripheral wall of the sliding valve; after being heated, the thermal sensing component can deform and drive the sliding valve to move axially along the main oil passage from the first working position to the second working position; when the thermal sensing component cools down, its shape resumes and drives the sliding valve to reset; in the first working position, along the flow direction of the lubricating oil, the primary oil inlet is located on the downstream side of the second oil distribution hole, and the primary oil inlet is communicated with the main oil hole through the second oil distribution hole, and the first oil distribution hole is not communicated with the primary oil inlet; in the second working position, the primary oil inlet is located on the downstream side of the first oil distribution hole, and the primary oil inlet is communicated with the main oil hole through the first oil distribution hole.

[0013] As can be seen from the above solution, the self-regulating oil pump system of the present invention controls the movement of the sliding valve by the thermal sensing structural member to realize the movement of the sliding valve between the first working position and the second working position, thereby controlling the flow rate of the lubricating oil entering the primary oil supply passage, so that the lubricating oil matches the working state. Since no redundant unbalanced eccentric structure is added, the self-regulating oil pump system will not generate redundant unbalanced inertial force, and it can adjust the oil flow rate through the temperature in the cavity of the compressor. When the compressor operates under high-frequency and high-speed conditions, the temperature in the compressor rises. When the working temperature exceeds the austenite start temperature line of the thermal sensing component, the self-regulating oil pump of the present invention starts to work, so that the primary oil inlet connecting the main oil passage and the primary oil supply passage is opened, and the amount of oil pumped upward through the primary oil supply passage increases, thereby increasing the amount of lubricating oil at the gap between the connecting rod, piston and cylinder arranged at the upper end of the crankshaft, thereby avoiding the wear and failure of the crankshaft, connecting rod, piston and cylinder, that is, improving the oil pumping volume under high-frequency conditions of the compressor, avoiding the problem that the components of the compressor pump body cannot form a stable oil film due to the reduction of the lubricating oil viscosity, resulting in wear between the components, and also improving the oil film sealing performance between the piston and the cylinder, reducing leakage, and improving the refrigeration performance under high-frequency conditions of the compressor.

[0014] In addition, even when the suction and discharge pressures of the compressor are above 1.5 MPa and the temperature inside the cavity under medium- and low-frequency operating conditions is relatively high, the self-regulating oil pump of the present invention will still operate, and the problem that the components of the compressor pump body cannot form a stable oil film due to the reduced viscosity of the lubricating oil, resulting in wear between the components, is also solved. The oil film sealing performance between the piston and the cylinder under medium- and low-frequency operating conditions is improved, leakage is reduced, and the refrigeration performance of the compressor under medium- and low-frequency operating conditions is improved.

[0015] At the same time, since no redundant unbalanced eccentric structure is added, the shafting balance structure of the original wide-frequency piston compressor pump body is not damaged, so the frictional power consumption, vibration, and noise of the wide-frequency piston compressor will not increase, improving the user experience.

[0016] A preferred solution is that an annular oil passage is further provided on the sliding valve. The annular oil passage is located on the outer peripheral wall of the sliding valve and extends along the circumferential direction of the sliding valve. The first oil distribution hole is located in the annular oil passage, and the annular oil passage is communicated with the main oil hole through the first oil distribution hole. When the sliding valve is in the first working position, the first oil inlet is arranged out of alignment with the annular oil passage. When the sliding valve is in the second working position, the first oil inlet is arranged opposite to the annular oil passage.

[0017] Thus, the setting of the second annular oil passage ensures that the oil pumped out from the first oil distribution hole can be stably supplied to the first upper oil passage.

[0018] A further solution is that the cross-section of the annular oil passage is trapezoidal, and the width of the annular oil passage gradually increases from the bottom wall of the annular oil passage to the opening of the annular oil passage.

[0019] Thus, the annular oil passage with a trapezoidal cross-section can increase the oil storage capacity.

[0020] A further solution is that the number of the first oil distribution holes is more than two, and each first oil distribution hole is arranged along the extending direction of the annular oil passage.

[0021] Thus, by setting a plurality of first oil distribution holes, the total cross-sectional area of the first oil distribution holes can be increased, thereby increasing the amount of lubricating oil flowing into the first upper oil passage during operation under high-frequency conditions.

[0022] A preferred solution is that the total cross-sectional area of the first oil distribution holes is larger than the total cross-sectional area of the second oil distribution holes.

[0023] Thus, it is ensured that the amount of oil pumped into the first upper oil passage in the second working position is greater than the amount of oil pumped into the first upper oil passage in the first working position.

[0024] A preferred solution is that the base material of the thermal sensing component is a shape memory alloy, and the austenite start temperature line of the shape memory alloy is greater than or equal to 65 °C; and / or the thermal sensing component is a thermal sensing spring.

[0025] Thus, by utilizing the reversible phase change of the microscopic crystal structure of the shape memory alloy under temperature change, the deformation of the thermal sensing component is realized, and further the movement of the sliding valve is promoted. It has high stability and does not require an additional driving part, which can reduce costs.

[0026] A further solution is that the shape memory alloy is a binary shape memory alloy or a ternary shape memory alloy; the shape memory alloy is a Ni-Ti based shape memory alloy, a Cu-based shape memory alloy or an Fe-based shape memory alloy.

[0027] A preferred solution is that the self-regulating oil pump assembly further includes an oil guiding pipe, the oil guiding pipe is arranged in the main oil passage and is in interference fit with the main oil passage; the thermal sensing component is located between the oil guiding pipe and the sliding valve, and the first end of the thermal sensing component is fixed to the oil guiding pipe; the oil guiding part is installed in the oil guiding pipe and is in clearance fit with the oil guiding pipe.

[0028] Thus, it can be seen that the oil guiding pipe can support and fix the thermal sensing component.

[0029] A preferred solution is that the oil guiding part is provided with an oil guiding channel spirally extending along the outer peripheral wall of the oil guiding part, and the oil guiding channel is communicated with the main oil passage.

[0030] Thus, it can be seen that the oil guiding part extends into the oil sump and continuously pumps the lubricating oil upward as the crankshaft rotates.

[0031] A preferred solution is that the oil guiding part has a hollow structure and is provided with a hollow groove, and the hollow groove is recessed inward along the axial direction of the oil guiding part from the end close to the thermal sensing component.

[0032] Thus, by setting the oil guiding part into a hollow structure, the weight of the overall structure can be reduced and the cost can be reduced.

[0033] A preferred solution is that the self-regulating oil pump system further includes a fixing frame, and the fixing frame is arranged at one end of the long shaft away from the short shaft; the oil guiding part is fixedly connected to the fixing frame, and the fixing frame is further provided with a fixing part.

[0034] Thus, it can be seen that by fixing and supporting the oil guiding part through the fixing frame, the self-rotation of the oil guiding part can be prevented.

[0035] A preferred solution is that the main oil hole is recessed inward along the axial direction of the sliding valve from the end close to the thermal sensing component; the first oil distribution hole is arranged at one end of the sliding valve close to the second oil distribution hole.

[0036] Preferably, the secondary oil supply passage includes a first oil distribution passage and a second oil distribution passage connected to each other. The main oil passage, the first oil distribution passage, and the second oil distribution passage are connected in sequence and their inner diameters decrease in sequence. The first oil distribution passage extends along the axial direction of the long axis, and the second oil distribution passage is inclined with respect to the axial direction of the long axis; and / or the primary oil supply passage includes a first spiral oil distribution passage, a third oil distribution passage, a fourth oil distribution passage, a fifth oil distribution passage, and a second spiral oil distribution passage connected in sequence. The first spiral oil distribution passage spirally extends along the outer peripheral wall of the long axis, the fourth oil distribution passage extends linearly and is inclined with respect to the axial direction of the long axis, the second spiral oil distribution passage spirally extends along the outer peripheral wall of the short axis, and the primary oil inlet is located on the first spiral oil distribution passage.

[0037] Further, a bevel step is formed at the connection between the main oil passage and the first oil distribution passage. The end wall of the sliding valve away from the thermal sensing component is conical, and the bevel step and the conical end wall of the sliding valve are opposite and are in limiting cooperation.

[0038] It can be seen that through the cooperation of the inclination angles of the two opposite bevels, the adjustment of the oil output of the second oil distribution hole is realized, and at the same time, the problem that the second oil distribution hole is blocked when the sliding valve moves to the position where it abuts against the step and the oil cannot be pumped into the secondary oil supply passage is avoided.

[0039] To achieve the above second object, the present invention provides a compressor including the above self-regulating oil pump system.

[0040] To achieve the above third object, the present invention provides a refrigeration device including the above compressor. Description of the Drawings

[0041] Figure 1 It is a cross-sectional view of an embodiment of the compressor of the present invention.

[0042] Figure 2 It is a structural diagram of the core component in an embodiment of the compressor of the present invention.

[0043] Figure 3 It is a structural diagram of the core in an embodiment of the compressor of the present invention.

[0044] Figure 4 It is a structural diagram of an embodiment of the self-regulating oil pump system of the present invention.

[0045] Figure 5 It is a cross-sectional view of an embodiment of the self-regulating oil pump system of the present invention.

[0046] Figure 6 It is an exploded structural view of the self-regulating oil pump component in an embodiment of the self-regulating oil pump system of the present invention.

[0047] Figure 7 It is a three-dimensional view of the crankshaft in an embodiment of the self-regulating oil pump system of the present invention.

[0048] Figure 8 It is the front view of the crankshaft in the embodiment of the self-regulating oil pump system of the present invention.

[0049] Figure 9 It is the perspective view of the oil guiding pipe in the embodiment of the self-regulating oil pump system of the present invention.

[0050] Figure 10 It is the front view of the oil guiding pipe in the embodiment of the self-regulating oil pump system of the present invention.

[0051] Figure 11 It is the structural diagram of the oil attracting part in the embodiment of the self-regulating oil pump system of the present invention.

[0052] Figure 12 It is the sectional view of the oil attracting part in the embodiment of the self-regulating oil pump system of the present invention.

[0053] Figure 13 It is the structural diagram of the sliding valve in the embodiment of the self-regulating oil pump system of the present invention.

[0054] Figure 14 It is the sectional view of the first position of the sliding valve in the embodiment of the self-regulating oil pump system of the present invention.

[0055] Figure 15 It is the sectional view of the second position of the sliding valve in the embodiment of the self-regulating oil pump system of the present invention.

[0056] Figure 16 It is the state diagram of the sliding valve in the first working position in the embodiment of the self-regulating oil pump system of the present invention.

[0057] Figure 17 It is the state diagram of the sliding valve during the movement from the first working position to the second working position in the embodiment of the self-regulating oil pump system of the present invention.

[0058] Figure 18 It is the state diagram of the sliding valve in the second working position in the embodiment of the self-regulating oil pump system of the present invention.

[0059] The present invention will be further described below in conjunction with the accompanying drawings and embodiments. Detailed Embodiments

[0060] Now, various exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and in no way limits the present invention and its application or use. The present invention can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the present invention thorough and complete and to fully convey the scope of the present invention to those skilled in the art. It should be noted that: unless otherwise specifically stated, the relative arrangements of components and steps, the compositions of materials, numerical expressions, and numerical values set forth in these embodiments should be construed as merely exemplary and not as limitations.

[0061] In the present invention, words such as "first", "second" and the like do not denote any order, quantity or importance, but are only used to distinguish different parts. Words such as "comprising" or "including" mean that the elements before this word cover the elements listed after this word, and do not exclude the possibility of also covering other elements. "Upper", "lower", "left", "right", etc. are only used to represent relative positional relationships. When the absolute position of the object being described changes, the relative positional relationship may also change accordingly.

[0062] In the present invention, when it is described that a specific device is located between a first device and a second device, there may or may not be an intermediate device between the specific device and the first device or the second device. When it is described that a specific device is connected to other devices, the specific device may be directly connected to the other devices without an intermediate device, or may not be directly connected to the other devices and have an intermediate device.

[0063] All terms used in the present invention (including technical terms or scientific terms) have the same meanings as those understood by ordinary technical personnel in the relevant field, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries should be interpreted as having meanings consistent with their meanings in the context of the relevant technology, and should not be interpreted in an idealized or overly formal sense, unless specifically defined as such here.

[0064] Technologies, methods and devices known to ordinary technical personnel in the relevant field may not be discussed in detail, but where appropriate, the said technologies, methods and devices should be regarded as part of the specification.

[0065] The refrigeration device in this embodiment is a refrigerator, and the refrigeration device includes a compressor, and the compressor is a piston compressor.

[0066] See Figures 1 to 3 , the compressor of this embodiment includes a housing assembly 100 and a core assembly 200. The core assembly 200 includes a core 210, a motor assembly 220 and a silencer assembly 230. The core 210 includes a cylinder block 211, a crankshaft 3, a counterweight 213, a connecting rod 214, a piston 215, a suction and discharge valve assembly 216, a cylinder head 217 and a self-regulating oil pump assembly 4. After the motor drives the crankshaft 3 to rotate, the piston 215 connected to the connecting rod 214 makes a reciprocating linear motion in the cylinder of the cylinder block 211, and then inhales and compresses the refrigerant gas to do work.

[0067] The crankshaft 3 and the self-regulating oil pump assembly 4 form a self-regulating oil pump system 5. The tail end of the crankshaft 3 and the tail end of the self-regulating oil pump assembly 4 in the self-regulating oil pump system 5 are both immersed in the oil sump 300 of the compressor, so as to achieve the effect of pumping oil.

[0068] The crankshaft 3 includes a long shaft 31, a crank 32 and a short shaft 33 which are connected in sequence. The long shaft 31 of the crankshaft 3 is rotationally matched with the shaft hole of the cylinder block 211, and the short shaft 33 of the crankshaft 3 is rotationally matched with the large shaft hole of the connecting rod 214. The self-adjusting oil pump system 5 provides good lubrication for the surfaces of these friction pairs such as between the long shaft 31 and the shaft hole of the cylinder block 211, between the short shaft 33 and the large shaft hole of the connecting rod 214, between the small shaft hole of the connecting rod 214 and the piston pin on the piston 215, and between the piston 215 and the cylinder of the cylinder block 211, and provides good oil film sealing between the piston 215 and the cylinder of the cylinder block 211, reduces the leakage of refrigerant gas, reduces the operating power consumption of the compressor, and improves the overall performance of the compressor.

[0069] See Figures 4 to 15 , a first oil supply passage 34 and a second oil supply passage 35 are formed on the crankshaft 3. A main oil passage 36 is formed at one end of the long shaft 31 away from the short shaft 33 (i.e., the tail end of the crankshaft 3). The first oil supply passage 34 has a first oil inlet 341 and a first oil outlet 342, and the second oil supply passage 35 has a second oil inlet 351 and a second oil outlet 352. The first oil inlet 341 and the second oil inlet 351 are both communicated with the main oil passage 36. The first oil outlet 342 is located on the short shaft 33, and the second oil outlet 352 is located on the end wall of the crank 32 facing the short shaft 33.

[0070] The second oil supply passage 35 includes a first oil distribution passage 353 and a second oil distribution passage 354 which are connected. The main oil passage 36, the first oil distribution passage 353 and the second oil distribution passage 354 are communicated in sequence and the inner diameters decrease in sequence. The first oil distribution passage 353 extends along the axial direction of the long shaft 31, and the second oil distribution passage 354 is inclined relative to the axial direction of the long shaft 31. The first oil supply passage 34 includes a first spiral oil distribution passage 343, a third oil distribution passage 344, a fourth oil distribution passage 345, a fifth oil distribution passage 346 and a second spiral oil distribution passage 347 which are connected in sequence. The first spiral oil distribution passage 343 extends spirally along the outer peripheral wall of the long shaft 31. The fourth oil distribution passage 345 extends linearly and is inclined relative to the axial direction of the long shaft 31. The second spiral oil distribution passage 347 extends spirally along the outer peripheral wall of the short shaft 33. The first oil inlet 341 is located on the first spiral oil distribution passage 343.

[0071] The self-regulating oil pump assembly 4 is installed in the main oil passage 36. The self-regulating oil pump assembly 4 includes a sliding valve 41, a thermal sensing component 42, an oil guiding component 43, and a guide oil pipe 44. The sliding valve 41, the thermal sensing component 42, and the oil guiding component 43 are arranged in sequence along the axial direction of the long axis 31. The guide oil pipe 44 is arranged in the main oil passage 36 and is in interference fit with the main oil passage 36. The oil guiding component 43 is installed in the guide oil pipe 44 and is in clearance fit with the guide oil pipe 44. The unilateral fit clearance between the oil guiding component 43 and the inner pipe wall 441 of the guide oil pipe 44 is 10 μm to 30 μm. The thermal sensing component 42 is located between the guide oil pipe 44 and the sliding valve 41. The first end of the thermal sensing component 42 is fixed to the guide oil pipe 44 by means of bonding, welding, or snap-fastening, etc. The second end of the thermal sensing component 42 is also fixedly connected to the sliding valve 41 by means of bonding, welding, or snap-fastening, etc.

[0072] See Figure 5 , and Figures 13 to 15 , a main oil hole 411, a first oil distribution hole 412, and a second oil distribution hole 413 are provided on the sliding valve 41. The main oil hole 411 is recessed inward from one end close to the thermal sensing component 42 along the axial direction of the sliding valve 41. Both the first oil distribution hole 412 and the second oil distribution hole 413 communicate with the main oil passage 36 through the main oil hole 411. The second oil distribution hole 413 is located on the end wall 410 of the sliding valve 41 away from the thermal sensing component 42. The secondary upper oil passage 35 communicates with the main oil hole 411 through the second oil distribution hole 413. The first oil distribution hole 412 is located on the peripheral wall of the sliding valve 41 and is provided at one end of the sliding valve 41 close to the second oil distribution hole 413.

[0073] An annular oil passage 414 is further provided on the sliding valve 41. The annular oil passage 414 is located on the outer peripheral wall of the sliding valve 41 and extends along the circumferential direction of the sliding valve 41. The first oil distribution hole 412 is located in the annular oil passage 414. The annular oil passage 414 communicates with the main oil hole 411 through the first oil distribution hole 412. The cross-section of the annular oil passage 414 is trapezoidal. Along the radial direction of the sliding valve 41, from the bottom wall of the annular oil passage 414 to the opening of the annular oil passage 414, the width of the annular oil passage 414 gradually increases.

[0074] The number, size, arrangement, etc. of the first oil distribution holes 412 and the second oil distribution holes 413 can all be changed as needed. Preferably, the number of the first oil distribution holes 412 is more than two. In this embodiment, the number of the first oil distribution holes 412 is four, and each of the first oil distribution holes 412 is arranged along the extending direction of the annular oil passage 414. The number of the second oil distribution holes 413 is three, and the total cross-sectional area of the four first oil distribution holes 412 is larger than the total cross-sectional area of the three second oil distribution holes 413, so as to ensure that the amount of oil pumped into the first-stage upper oil passage 34 in the second working position is greater than the amount of oil pumped into the first-stage upper oil passage 34 in the first working position. In other embodiments, the total cross-sectional area of each of the first oil distribution holes 412 does not necessarily have to be larger than the total cross-sectional area of each of the second oil distribution holes 413, as long as it satisfies that the amount of oil pumped into the first-stage upper oil passage 34 when the sliding valve 41 is in the second working position is greater than the amount of oil pumped into the first-stage upper oil passage 34 when the sliding valve 41 is in the first working position.

[0075] A bevel step 37 is formed at the connection between the main oil passage 36 and the first oil distribution passage 353. The end wall 410 of the sliding valve 41 away from the heat sensing component 42 is conical, and the bevel step 37 and the conical end wall 410 of the sliding valve 41 are opposite and in limiting fit. Through the cooperation of the inclination angles of the two opposite bevels, the adjustment of the oil output of the second oil distribution holes 413 is realized, and at the same time, the problem that the second oil distribution holes 413 are blocked when the sliding valve 41 moves to the position where it abuts against the step and the oil cannot be pumped into the second-stage upper oil passage 35 is avoided.

[0076] The heat sensing component 42 is a heat sensing spring, and the base material of the heat sensing spring is a shape memory alloy. The austenite start temperature line Ac of the shape memory alloy is greater than or equal to 65°C. The shape memory alloy is a binary shape memory alloy or a ternary shape memory alloy, and the shape memory alloy is a Ni-Ti based shape memory alloy, a Cu-based shape memory alloy or an Fe-based shape memory alloy. The shape memory alloy has a shape memory effect (SME) and superelasticity (SE). The so-called shape memory effect (SME) refers to the ability of the shape memory alloy (SMAs) after cooling deformation to be heated to restore its original shape, which is the recovery caused by reversible martensitic transformation. The so-called superelasticity (SE) refers to the ability of the material to generate a strain far exceeding the elastic limit after plastic deformation and to completely restore its original shape after removing the stress. The austenite start temperature line Ac of the shape memory alloy is within the range of the operating temperature of the compressor. The actual operating temperature of the compressor is about room temperature to 200°C. When the temperature inside the compressor is higher than this austenite start temperature line Ac, the shape memory alloy will gradually transform from the martensite phase to the austenite phase; when the temperature inside the compressor is lower than this austenite start temperature line Ac, the shape memory alloy will gradually transform from the austenite phase to the martensite phase. By utilizing the reversible phase transformation of the microstructure crystal structure of the shape memory alloy with temperature change, the deformation of the heat sensing component 42 is realized, and then the movement of the sliding valve 41 is promoted. It has high stability and does not require an additional driving component, which can reduce costs.

[0077] After the heat-sensitive component 42 is heated, it can deform and drive the sliding valve 41 to move axially along the main oil passage 36 from the first working position to the second working position. After the heat-sensitive component 42 cools, its shape is restored and it drives the sliding valve 41 to reset.

[0078] In the first working position, the sliding valve 41 is separated from the inclined step 37, the primary oil inlet 341 is arranged out of alignment with the annular oil passage 414, the first oil distribution hole 412 is not communicated with the primary oil inlet 341, and along the flow direction of the lubricating oil, the primary oil inlet 341 is located on the downstream side of the second oil distribution hole 413. The primary oil inlet 341 is communicated with the main oil hole 411 through the second oil distribution hole 413.

[0079] In the second working position, the sliding valve 41 abuts against the inclined step 37, the primary oil inlet 341 is arranged opposite to the annular oil passage 414, the primary oil inlet 341 is located on the downstream side of the first oil distribution hole 412, and the primary oil inlet 341 is communicated with the main oil hole 411 through the first oil distribution hole 412.

[0080] The oil guiding member 43 is provided with a spiral boss 430 that spirally extends along the outer peripheral wall of the oil guiding member 43 to form an oil guiding channel 431 that spirally extends along the outer peripheral wall of the oil guiding member 43. The oil guiding channel 431 is communicated with the main oil passage 36. The oil guiding member 43 extends into the oil sump 300 and rotates with the crankshaft 3 driving the oil guiding member 43, continuously conveying the lubricating oil upward. The oil guiding member 43 has a hollow cylindrical structure. A hollow groove 432 is provided inside the oil guiding member 43. The hollow groove 432 is recessed inward along the axial direction of the oil guiding member 43 from one end close to the heat-sensitive component 42. By setting the oil guiding member 43 as a hollow structure, the weight of the overall structure can be reduced and the cost can be reduced.

[0081] The self-regulating oil pump system 5 further includes a fixing bracket 6. The fixing bracket 6 is arranged at one end of the long shaft 31 away from the short shaft 33. The oil guiding member 43 is fixedly connected to the fixing bracket 6. Specifically, a fixing ear 433 is provided on the bottom wall of the oil guiding member 43, a fixing hole 62 is provided in the middle of the fixing bracket 6, and a fixing pin 7 passes through the fixing ear 433 and the fixing hole 42 to fixedly connect the oil guiding member 43 to the fixing bracket 6. A fixing portion 61 is also provided on the fixing bracket 6. The fixing portion 61 is used for fixing to the housing of the motor assembly 220. By fixing and supporting the oil guiding member 43 through the fixing bracket 6, the self-rotation of the oil guiding member 43 can be prevented.

[0082] The working method of the self-regulating oil pump system 5 of the piston compressor for automatically adjusting the oil quantity of the lubricating oil pump according to the operating conditions of the compressor includes the following steps:

[0083] First, after the compressor is started, the lubricating oil at the bottom of the compressor is conveyed upward along the primary oil feeding channel 34 and the secondary oil feeding channel 35 on the crankshaft 3 under the action of the oil guiding member 43 at the bottom end of the crankshaft 3 and the oil guiding pipe 44.

[0084] See Figures 16 to 18 Figures 16 to 18 , when the pressure difference between the suction pressure and the discharge pressure of the compressor is below 1.5 MPa, as the compressor gradually operates under high-frequency and high-speed conditions, the oil temperature of the lubricating oil inside the compressor also gradually increases. When the temperature exceeds 65 °C, which is the temperature of the austenite start temperature line Ac of the shape memory alloy, the thermal induction spring of the shape memory alloy substrate begins to deform and elongate, driving the sliding valve 41 to move upward, making the annular oil passage 414 correspond to the primary oil inlet 341, increasing the oil pumping volume. At this time, it is in a gradually open flow state. As the compressor gradually operates under low-frequency and low-speed conditions, the oil temperature of the lubricating oil inside the compressor also gradually decreases. When the temperature drops below 65 °C, which is the temperature of the austenite start temperature line Ac of the shape memory alloy, the thermal induction spring of the shape memory alloy substrate begins to recover and deform to shorten, driving the sliding valve 41 to move downward, making the primary oil inlet 341 misaligned with the annular oil passage 414, and the first oil distribution hole 412 is not connected to the primary oil inlet 341. The lubricating oil can only flow into the primary oil inlet 341 through the second oil distribution hole 413, and the oil pumping volume gradually decreases. At this time, it is in a gradually throttling state. That is, as the rotational speed of the crankshaft 3 increases or decreases, the temperature also gradually increases or decreases, and the height of the sliding valve 41 increases or decreases accordingly. Furthermore, the self-regulating oil pumping system can automatically adjust the oil pumping volume of the compressor according to the operating conditions of the compressor.

[0085] When the pressure difference between the suction pressure and the discharge pressure of the compressor is below 1.5 MPa, the temperature inside the compressor is relatively high when the compressor operates at medium speed. However, when the compressor operates from low speed to medium speed, when the oil temperature of the lubricating oil inside the compressor exceeds 65 °C, which is the temperature of the austenite start temperature line Ac of the shape memory alloy, the thermal induction spring of the shape memory alloy substrate begins to deform and elongate, driving the sliding valve 41 to move upward, making the annular oil passage 414 correspond to the primary oil inlet 341, increasing the oil pumping volume. At this time, it is in a gradually open flow state. As the compressor gradually operates under low-frequency and low-speed conditions, the oil temperature of the lubricating oil inside the compressor also gradually decreases. When the temperature drops below 65 °C, which is the temperature of the austenite start temperature line Ac of the shape memory alloy, the thermal induction spring of the shape memory alloy substrate begins to recover and deform to shorten, driving the sliding valve 41 to move downward, making the primary oil inlet 341 misaligned with the annular oil passage 414, and the first oil distribution hole 412 is not connected to the primary oil inlet 341. The lubricating oil can only flow into the primary oil inlet 341 through the second oil distribution hole 413, and the oil pumping volume gradually decreases. At this time, it is in a gradually throttling state. That is, as the rotational speed of the crankshaft 3 increases or decreases, the temperature also gradually increases or decreases, and the height of the sliding valve 41 increases or decreases accordingly. Furthermore, the self-regulating oil pumping system can automatically adjust the oil pumping volume of the compressor according to the operating conditions of the compressor.

[0086] Meanwhile, as the height of the sliding valve 41 increases or decreases, the cross-sectional area of the oil passage connecting the primary oil inlet 341 and the annular oil passage 414 increases or decreases accordingly, thereby achieving the purpose of automatically adjusting the oil pumping volume of the compressor according to the working pressure and operating conditions of the compressor.

[0087] As can be seen from the above, the self-regulating oil pump system of the present invention controls the movement of the sliding valve by the thermal sensing structural member to realize the movement of the sliding valve between the first working position and the second working position, and further controls the flow rate of the lubricating oil entering the primary upper oil passage, so that the lubricating oil matches the working state. Since no redundant unbalanced eccentric structure is added, the self-regulating oil pump system will not generate redundant unbalanced inertial forces, and it can adjust the oil flow rate through the cavity temperature of the compressor. When the compressor operates under high-frequency and high-speed conditions, the temperature inside the compressor rises. When the working temperature exceeds the austenite start temperature line of the thermal sensing component, the self-regulating oil pump of the present invention starts to work, so that the primary oil inlet connecting the main oil passage and the primary upper oil passage is opened. Since the total cross-sectional area of the first oil distribution holes is large, more oil is pumped upward through the primary upper oil passage, thereby increasing the amount of lubricating oil at the gaps between the connecting rod, piston and cylinder arranged at the upper end of the crankshaft, and further avoiding the wear and failure of the crankshaft, connecting rod, piston and cylinder, that is, improving the oil pumping volume of the compressor under high-frequency conditions, avoiding the problem that the components of the compressor pump body cannot form a stable oil film due to the decrease in the viscosity of the lubricating oil, resulting in wear between the components, and also improving the oil film sealing performance between the piston and the cylinder, reducing leakage, and improving the refrigeration performance of the compressor under high-frequency conditions.

[0088] In addition, when the wide-frequency piston compressor operates under high-frequency conditions with a high pressure difference (△P above 1.5 MPa), even if the compressor operates at medium and low speeds under medium and low conditions, the temperature inside the compressor will still be relatively high at this time. Especially when operating under medium-frequency conditions, the temperature will be much higher than that under medium-frequency conditions with a lower original pressure difference, which will lead to a decrease in the viscosity of the lubricating oil inside the compressor, so that a stable lubricating oil film cannot be formed between the components to avoid wear of the components, and also avoid the leakage problem between the piston and the cylinder. Therefore, even when the compressor is under medium and low-frequency conditions, the self-regulating oil pump of the present invention will work, and the problem that the components of the compressor pump body cannot form a stable oil film due to the decrease in the viscosity of the lubricating oil, resulting in wear between the components, is also solved. The oil film sealing performance between the piston and the cylinder under medium and low-frequency conditions is improved, leakage is reduced, and the refrigeration performance of the compressor under medium and low-frequency conditions is improved.

[0089] Meanwhile, since no redundant unbalanced eccentric structure is added, the shafting balance structure of the original wide-frequency piston compressor pump body is not damaged, and thus the friction power consumption, vibration and noise of the wide-frequency piston compressor will not be increased, improving the user experience.

[0090] Finally, it should be emphasized that the above are only the preferred embodiments of the present invention and are not used to limit the present invention. For those skilled in the art, the present invention can have various changes and modifications. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. Self-regulating oil pump system, including crankshaft; The crankshaft comprises a long shaft, a crank and a short shaft connected in sequence, a primary oiling channel and a secondary oiling channel are provided on the crankshaft, and a main oil passage is provided at one end of the long shaft away from the short shaft; The primary oil passage has a primary oil inlet and a primary oil outlet, the secondary oil passage has a secondary oil inlet and a secondary oil outlet, the primary oil inlet and the secondary oil inlet are both connected to the main oil passage, the primary oil outlet is located on the short shaft, and the secondary oil outlet is located on the end wall of the crank facing the short shaft; Features: The self-regulating oil pump system further comprises a self-regulating oil pump assembly, wherein the self-regulating oil pump assembly is installed in the main oil gallery; The self-regulating oil pump assembly comprises a sliding valve, a heat sensing component and an oil guide member which are sequentially arranged along the axial direction of the long axis; The first end of the heat-sensing component is fixed relative to the long axis, and the second end of the heat-sensing component is connected to the sliding valve; The sliding valve is provided with a main oil hole, a first oil distribution hole and a second oil distribution hole, the first oil distribution hole and the second oil distribution hole are both connected to the main oil channel through the main oil hole, the second oil distribution hole is located on the end wall of the sliding valve away from the heat-sensitive component, the secondary oil supply channel is connected to the main oil hole through the second oil distribution hole, and the first oil distribution hole is located on the peripheral wall of the sliding valve; The heat-sensitive component is deformed after being heated and drives the sliding valve to move from the first working position to the second working position along the axial direction of the main oil channel. The heat-sensitive component recovers its shape after being cooled and drives the sliding valve to return to its original position. In the first working position, the primary oil inlet is connected to the main oil hole through the second oil distribution hole, and the first oil distribution hole is not connected to the primary oil inlet; In the second working position, the primary oil inlet is connected to the main oil hole through the first oil distribution hole; When the sliding valve is in the second working position, the amount of oil pumped into the primary upper oil channel is greater than the amount of oil pumped into the primary upper oil channel when the sliding valve is in the first working position.

2. The self-regulating oil pump system according to claim 1, characterized in that: The sliding valve is also provided with an annular oil passage, which is located on the outer peripheral wall of the sliding valve and extends along the circumference of the sliding valve, the first oil distribution hole is located in the annular oil passage, and the annular oil passage is connected with the main oil hole through the first oil distribution hole; When the sliding valve is located at the first working position, the primary oil inlet and the annular oil passage are arranged in a staggered manner; When the sliding valve is located at the second working position, the primary oil inlet is arranged opposite to the annular oil passage.

3. The self-regulating oil pump system according to claim 2, characterized in that: The cross section of the annular oil channel is trapezoidal, and the width of the annular oil channel gradually increases from the bottom wall of the annular oil channel to the opening of the annular oil channel.

4. The self-regulating oil pump system according to claim 2, characterized in that: The number of the first oil distribution holes is more than two, and each of the first oil distribution holes is arranged along the extending direction of the annular oil passage.

5. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The total cross-sectional area of ​​the first oil-dividing holes is greater than the total cross-sectional area of ​​the second oil-dividing holes.

6. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The base material of the thermal sensing component is a memory alloy, and the austenite starting temperature line of the memory alloy is greater than or equal to 65° C.; and / or The thermal induction component is a thermal induction spring.

7. The self-regulating oil pump system according to claim 6, characterized in that: The memory alloy is a binary memory alloy or a ternary memory alloy; The memory alloy is a Ni-Ti based memory alloy, a Cu based memory alloy or a Fe based memory alloy.

8. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The self-regulating oil pump assembly further comprises an oil guide pipe, which is arranged in the main oil passage and has an interference fit with the main oil passage; The heat-sensing component is located between the oil-conducting pipe and the sliding valve, and a first end of the heat-sensing component is fixed to the oil-conducting pipe; The oil guiding member is installed in the oil guiding pipe and is in clearance fit with the oil guiding pipe.

9. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The oil introducing member is provided with an oil introducing passage which spirally extends along the outer peripheral wall of the oil introducing member, and the oil introducing passage is communicated with the main oil passage.

10. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The oil guiding member is of a hollow structure.

11. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The self-regulating oil pump system further comprises a fixing frame, wherein the fixing frame is arranged at an end of the long shaft away from the short shaft; The oil guide piece is fixedly connected to the fixing frame, and a fixing portion is also arranged on the fixing frame.

12. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The main oil hole is recessed inwardly along the axial direction of the sliding valve from an end close to the heat-sensing component; The first oil distribution hole is arranged on one end of the sliding valve close to the second oil distribution hole.

13. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The secondary oiling channel comprises a first oil branch channel and a second oil branch channel connected to each other, the main oil channel, the first oil branch channel and the second oil branch channel are connected in sequence and the inner diameters are reduced in sequence, the first oil branch channel extends along the axial direction of the long axis, and the second oil branch channel is inclined relative to the axial direction of the long axis; and / or The first-level oil channel includes a first spiral oil channel, a third oil channel, a fourth oil channel, a fifth oil channel and a second spiral oil channel connected in sequence. The first spiral oil channel extends in a spiral along the outer peripheral wall of the major axis, the fourth oil channel extends in a straight line and is inclined relative to the axial direction of the major axis, the second spiral oil channel extends in a spiral along the outer peripheral wall of the minor axis, and the first-level oil inlet is located on the first spiral oil channel.

14. The self-regulating oil pump system according to claim 13, characterized in that: An inclined step is formed at the connection between the main oil passage and the first branch oil passage, the end wall of the sliding valve away from the heat-sensitive component is conical, and the inclined step is opposite to the conical end wall of the sliding valve and is limitedly matched.

15. A compressor, characterized in that Comprising a self-regulating oil pump system as claimed in any one of claims 1 to 14.

16. Refrigeration equipment, characterized in that Comprising the compressor of claim 15.

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