Self-regulating oil pump system, compressor and refrigeration appliance

Abstract

The application provides a self-adjusting oil pump system, a compressor and a refrigeration device, the self-adjusting oil pump system comprising a crankshaft and a self-adjusting oil pump assembly; the self-adjusting oil pump assembly comprising a sliding valve, a heat-sensitive component and an oil guiding part arranged along the axis of the long shaft in sequence; the heat-sensitive component can be deformed after being heated and drive the sliding valve to move along the axis of the main oil passage from a first working position to a second working position; in the first working position, the first-stage 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 first-stage oil inlet; in the second working position, the first-stage oil inlet is communicated with the main oil hole through the first oil distribution hole. The self-adjusting oil pump system solves the problem that the existing technology produces unbalanced inertia force in the rotating process, which leads to the increase of the operating power consumption of the compressor, the increase of the compressor and the intensification of the noise, and solves the problem that the insufficient oil pumping amount leads to the wear and leakage of the parts when the existing compressor operates under the high-frequency working condition or under the high-pressure difference working condition.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to a self-adjusting oil pump system, a compressor and a refrigeration device. BACKGROUND

[0002] For a reciprocating piston compressor, the suction and exhaust valve assembly, the cylinder on the cylinder head and the piston that can make linear reciprocating motion form a closed compression chamber. The cylinder head completely covers the suction and exhaust valve assembly to form a closed exhaust chamber. When the piston makes linear reciprocating motion in the cylinder, the refrigerant gas in the piston compressor housing can be sucked in, then the refrigerant gas is compressed and worked, and then the compressed refrigerant gas is discharged into the exhaust chamber, thereby forming a cycle of suction, compression and exhaust. Finally, the high-pressure refrigerant gas in the exhaust chamber is transported to the outside of the compressor through the internal exhaust coil pipe and enters the refrigeration cycle system of the refrigerator.

[0003] When the refrigerator needs to quickly reach the instant freezing effect of-35℃, the piston compressor needs to operate at a high frequency of 100Hz or more. With the rapid increase of the operating frequency of the compressor, higher requirements are put forward for the oil lubrication between the parts of the compressor, that is, more lubricating oil is needed between the parts under high-frequency working conditions to form a stable oil film to avoid wear between the parts. Therefore, the pump oil volume of the compressor needs to be increased under high-frequency working conditions. To increase the pump oil volume, a spiral pump oil structure is generally added to the lower end of the crankshaft of the piston compressor. For example, a pump oil device suitable for a wide range of compressor speeds. Although this spiral pump oil structure can increase the pump oil volume of the compressor under high-frequency working conditions, it also increases the pump oil volume under medium and low-frequency working conditions, that is, it cannot adjust the pump oil volume according to the different operating frequencies of the compressor. When the refrigerator door is closed, the compressor will operate at a low frequency of 33Hz or less for a long time. Under low-frequency working conditions, the lubricating oil on the spiral oil pump not only lubricates the parts, but also forms an oil-gas mixture with the refrigerant gas, that is, the more the pump oil volume of the spiral pump oil structure under low-frequency working conditions, the greater the proportion of the oil-gas mixture in the compression chamber, and the smaller the proportion of the refrigerant gas, which leads to a decrease in the volumetric efficiency of the compression chamber under low-frequency working conditions, and ultimately leads to a decrease in the refrigeration capacity of the compressor under low-frequency working conditions.

[0004] In order to simultaneously reduce the pump oil volume of the compressor under low-frequency working conditions and increase the pump oil volume of the compressor under high-frequency working conditions, there are currently three variable oil volume adjustment technologies for small piston compressors.

[0005] The first kind is to add an unbalanced plug connected by a spring in the main oil passage of the crankshaft. The unbalanced plug will block the oil distribution hole connected with the spiral oil distribution passage as the rotating speed of the crankshaft increases, that is, the unbalanced plug realizes the opening and closing of the oil distribution hole on 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 in a high-frequency high-speed working condition, the temperature in the compressor can reach above 100°C, thereby causing the viscosity of the lubricating oil to decrease by a large margin. At this time, the oil pumping amount is small, and a stable lubricating oil film cannot be formed between the compressor parts to avoid wear of the parts. At this time, the self-adjusting structure has been closed, and it cannot provide more lubricating oil to the parts of the pump body to improve the lubrication and oil film sealing between the parts. The parts are at risk of being worn, and the sealing effect between the piston and the cylinder formed by the oil film is also weakened, the leakage is intensified, and the refrigeration performance of the compressor is also reduced. At the same time, since the upper end of the axial direction of the main oil passage of the crankshaft is also provided with the oil distribution passage, the upper end of the spring of the self-adjusting oil pump structure is not subjected to the limiting action. During the high-speed rotation of the crankshaft, the plug connected by the spring may directly move upward and not block the oil distribution hole connected with the spiral oil distribution passage of the crankshaft, that is, the self-adjusting oil pump structure fails to open or close.

[0006] The second kind of self-adjusting oil pump structure is a combination structure of a valve plate and a counterweight. The counterweight is arranged outside the valve plate. As the rotating speed increases, the counterweight is driven by the centrifugal force to open the valve plate, thereby improving the oil pumping amount, that is, the oil film lubrication and sealing between the parts of the compressor in a high-frequency working condition are guaranteed. However, when the pressure difference between the suction and discharge pressures of the compressor is above 1.5 MPa, and the compressor is operating in a low-speed working condition, the self-adjusting oil pump structure that adjusts and switches through the rotating speed does not start to work, that is, the valve plate that controls the oil flow is still in a closed state. At this time, the temperature in the compressor is also relatively high, thereby causing the viscosity of the lubricating oil in the compressor to decrease. At this time, the oil pumping amount is small, and a stable lubricating oil film cannot be formed between the parts to avoid wear of the parts. At the same time, the self-adjusting oil pump structure is more complex, more parts are used, and the reliability cannot be guaranteed.

[0007] The third kind is that an oil inlet is arranged at the bottom of the liftable slide valve, an oil ring matched with a spiral oil distribution channel is arranged at the outer ring of the top of the slide valve, an oil hole communicated with the inner cavity of the slide valve is arranged on the oil ring, the lifting height of the slide valve is smaller than the sum of the diameter of the spiral oil distribution channel communicated with the spiral oil channel and the diameter of the oil hole communicated with the inner cavity of the slide valve, and a guide pipe with a spiral oil pump is further arranged at the bottom of the slide valve to increase the pump oil amount. At low rotating speed, the pump oil amount is small, the slide valve is partially lifted, and the oil ring between the spiral oil distribution channel communicated with the main oil channel and the spiral oil distribution channel and the slide valve is in a throttling state; with the increase of the rotating speed of the crankshaft, the pump oil amount is increased, the slide valve is lifted, and the oil ring between the spiral oil distribution channel communicated with the main oil channel and the spiral oil distribution channel and the oil ring is in a completely connected state. However, when the pressure difference of suction and discharge of the compressor is above 1.5 MPa and the compressor is in low-speed operation under medium and low frequency working conditions, the structure of the self-adjusting oil pump is controlled to be in a throttling state through the rotating speed, but at this time, the temperature in the compressor is also relatively high, thereby causing the decrease of the viscosity of the lubricating oil in the compressor, and at this time, the pump oil amount is small, thereby failing to form a stable lubricating oil film between the parts to avoid the wear of the parts.

[0008] Moreover, the first kind and the second kind are both through centrifugal force to make the unbalanced structure realize the opening and closing effect, but the unbalanced block increases the excessive unbalanced inertia force, thereby increasing the power loss caused by the unbalanced force, and also causing the increase of the friction force between the crankshaft of the compressor and the cylinder block, the increase of the friction power consumption, the increase of the vibration of the compressor, the increase of the noise, and the influence on the experience of the user. An additional balancing structure needs to be added to balance the unbalanced inertia force, but this also causes the structure of the compressor to be more complex and the reliability to be more difficult to guarantee. SUMMARY

[0009] The first object of the present application is to provide a self-adjusting oil pump system which solves the problems that the existing self-adjusting oil pump structure generates unbalanced inertia force during rotation, thereby causing the increase of the operating power consumption of the compressor, the increase and the noise.

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

[0011] The third object of the present application is to provide a refrigeration equipment adopting the compressor.

[0012] To achieve the above first object, the application provides a self-adjusting oil pump system, comprising a crankshaft; the crankshaft comprises a long shaft, a crank and a short shaft connected in sequence, and the crankshaft is provided with a first-stage oil feeding channel and a second-stage oil feeding channel; the long shaft is provided with a main oil passage at an end away from the short shaft; the first-stage oil feeding channel is provided with a first-stage oil inlet and a first-stage oil outlet; the second-stage oil feeding channel is provided with a second-stage oil inlet and a second-stage oil outlet; the first-stage oil inlet and the second-stage oil inlet are communicated with the main oil passage; the first-stage oil outlet is located on the short shaft; and the second-stage oil outlet is located on an end wall of the crank facing the short shaft; the self-adjusting oil pump system further comprises a self-adjusting oil pump assembly installed in the main oil passage; the self-adjusting oil pump assembly comprises a sliding valve, a thermal sensing component and an oil guiding piece 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; the second end of the thermal sensing component is connected with 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 communicated with the main oil passage through the main oil hole; the second oil distribution hole is located on an end wall of the sliding valve away from the thermal sensing component; the second-stage oil feeding channel is communicated with the main oil hole through the second oil distribution hole; and the first oil distribution hole is located on a peripheral wall of the sliding valve; the thermal sensing component can be deformed after being heated and drive the sliding valve to move along the axial direction of the main oil passage from a first working position to a second working position; the thermal sensing component can restore its shape after being cooled and drive the sliding valve to reset; in the first working position, along the flow direction of the lubricating oil, the first-stage oil inlet is located on the downstream side of the second oil distribution hole; the first-stage 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 first-stage oil inlet; in the second working position, the first-stage oil inlet is located on the downstream side of the first oil distribution hole; and the first-stage oil inlet is communicated with the main oil hole through the first oil distribution hole.

[0013] As can be seen from the above scheme, the self-adjusting oil pump system of the application controls the movement of the sliding valve through the thermal sensing structure to realize the movement of the sliding valve between the first working position and the second working position, thereby controlling the flow of the lubricating oil into the first-stage oil feeding channel, so that the lubricating oil is matched with the working state. Since no additional unbalanced eccentric structure is added, the self-adjusting oil pump system does not generate additional unbalanced inertia force, and it can adjust the oil flow through the temperature in the cavity of the compressor; when the compressor operates in a high-frequency high-speed working condition, the temperature in the compressor rises; when the working temperature exceeds the austenite starting temperature line of the thermal sensing component, the self-adjusting oil pump of the application starts to work, so that the first-stage oil inlet between the main oil passage and the first-stage oil feeding channel is opened, the oil pumped upward through the first-stage oil feeding channel is increased, thereby increasing the amount of lubricating oil at the gap between the connecting rod, the piston and the cylinder provided on the upper end of the crankshaft, thereby avoiding the wear and failure of the crankshaft, the connecting rod, the piston and the cylinder, i.e. improving the oil pumping amount of the compressor in a high-frequency working condition, avoiding the problem that the parts of the compressor pump body cannot form a stable oil film due to the reduction of the lubricating oil viscosity, causing wear between the parts, improving the oil film sealing performance between the piston and the cylinder, reducing leakage, and improving the refrigeration performance of the compressor in a high-frequency working condition.

[0014] In addition, even if the suction and discharge pressures of the compressor are above 1.5 MPa, and the temperature in the cavity of the compressor under medium and low frequency working conditions is relatively high, the self-adjusting oil pump of the application can still work, and the problem of wear between parts due to the reduction of the viscosity of the lubricating oil and the inability to form a stable oil film is solved, the oil film sealing performance between the piston and the cylinder under medium and low frequency working conditions is improved, the leakage is reduced, and the refrigeration performance of the compressor under medium and low frequency working conditions is improved.

[0015] At the same time, since no additional unbalanced eccentric structure is added, the shaft balance structure of the original wideband piston compressor pump body is not damaged, and the friction power consumption, vibration and noise of the wideband piston compressor are not increased, and the user experience is improved.

[0016] A preferred scheme is that the sliding valve is further provided with an annular oil channel, the annular oil channel 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 channel, and the annular oil channel communicates with the main oil hole through the first oil distribution hole; when the sliding valve is located at the first working position, the first-stage oil inlet is arranged in a staggered manner with the annular oil channel; and when the sliding valve is located at the second working position, the first-stage oil inlet is arranged in a relative manner with the annular oil channel.

[0017] Therefore, the arrangement of the second annular oil channel ensures that the oil pumped out from the first oil distribution hole can be stably supplied to the first-stage oil supply channel.

[0018] A further scheme is 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.

[0019] Therefore, the annular oil channel with a trapezoidal cross section can increase the oil storage capacity.

[0020] A further scheme is that the number of the first oil distribution holes is two or more, and each first oil distribution hole is arranged along the extension direction of the annular oil channel.

[0021] Therefore, by arranging a plurality of first oil distribution holes, the total cross-sectional area of the first oil distribution holes can be increased, so that the amount of lubricating oil flowing into the first-stage oil supply channel when operating under high frequency working conditions can be increased.

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

[0023] Therefore, it is ensured that the amount of oil pumped into the first-stage oil supply channel when the sliding valve is located at the second working position is greater than the amount of oil pumped into the first-stage oil supply channel when the sliding valve is located at the first working position.

[0024] In one preferred embodiment, the base material of the thermal responsive component is a memory alloy, and the austenite starting temperature of the memory alloy is greater than or equal to 65 DEG C; and / or the thermal responsive component is a thermal responsive spring.

[0025] Therefore, the reversible phase change of the microcrystal structure of the memory alloy under temperature change is utilized to realize the deformation of the thermal responsive component, and then the movement of the sliding valve is pushed, which is high in stability and does not need to additionally set a driving member, thereby reducing the cost.

[0026] In a further embodiment, the memory alloy is a binary memory alloy or a ternary memory alloy; and the memory alloy is a Ni-Ti memory alloy, a Cu-based memory alloy or a Fe-based memory alloy.

[0027] In one preferred embodiment, the self-adjusting oil pump assembly further comprises an oil guide pipe, which is arranged in the main oil channel and is in interference fit with the main oil channel; the thermal responsive component is located between the oil guide pipe and the sliding valve, and the first end of the thermal responsive component is fixed with the oil guide pipe; and the oil guide member is installed in the oil guide pipe and is in clearance fit with the oil guide pipe.

[0028] Therefore, the oil guide pipe can support and fix the thermal responsive component.

[0029] In one preferred embodiment, the oil guide member is provided with an oil guide channel which extends spirally along the outer peripheral wall of the oil guide member, and the oil guide channel is in communication with the main oil channel.

[0030] Therefore, the oil guide member extends into the oil pool and continuously pumps the lubricating oil upward along with the rotation of the crankshaft.

[0031] In one preferred embodiment, the oil guide member is of a hollow structure and is provided with a hollow groove which is recessed inward along the axial direction of the oil guide member from the end close to the thermal responsive component.

[0032] Therefore, the oil guide member is arranged in a hollow structure, which can reduce the weight of the overall structure and reduce the cost.

[0033] In one preferred embodiment, the self-adjusting oil pump system further comprises a fixing frame which is arranged at the end of the long shaft away from the short shaft; the oil guide member is fixedly connected with the fixing frame, and the fixing frame is further provided with a fixing portion.

[0034] Therefore, the fixing frame can fix and support the oil guide member, thereby preventing the oil guide member from rotating.

[0035] In one preferred embodiment, the main oil hole is recessed inward along the axial direction of the sliding valve from the end close to the thermal responsive component; and the first oil distribution hole is arranged at the end of the sliding valve close to the second oil distribution hole.

[0036] A preferred scheme is that the secondary oil feeding channel comprises a first sub-oil channel and a second sub-oil channel connected in sequence, the main oil channel, the first sub-oil channel and the second sub-oil channel are communicated in sequence and have diameters decreasing in sequence, the first sub-oil channel extends along the axial direction of the long shaft, and the second sub-oil channel is arranged obliquely relative to the axial direction of the long shaft; and / or the primary oil feeding channel comprises a first spiral sub-oil channel, a third sub-oil channel, a fourth sub-oil channel, a fifth sub-oil channel and a second spiral sub-oil channel connected in sequence, the first spiral sub-oil channel extends spirally along the outer peripheral wall of the long shaft, the fourth sub-oil channel extends linearly and is arranged obliquely relative to the axial direction of the long shaft, and the second spiral sub-oil channel extends spirally along the outer peripheral wall of the short shaft, and the primary oil inlet is located on the first spiral sub-oil channel.

[0037] A further scheme is that a bevel step is formed at the connection between the main oil channel and the first sub-oil channel, and the end wall of the sliding valve away from the heat-sensitive component is conical, the bevel step is opposite to the conical end wall of the sliding valve and is limited and matched.

[0038] Therefore, by matching the inclination angles of the two opposite bevels, the oil output of the second sub-oil hole is adjusted, and the problem that the second sub-oil hole is blocked when the sliding valve moves to the position abutting against the step and cannot pump oil to the secondary oil feeding channel is avoided.

[0039] To achieve the above-mentioned second object, the present application provides a compressor comprising the self-adjusting oil pump system.

[0040] To achieve the above-mentioned third object, the present application provides a refrigeration device comprising the compressor. BRIEF DESCRIPTION OF DRAWINGS

[0041] Figure 1 is a sectional view of an embodiment of the compressor of the present application.

[0042] Figure 2 is a structural diagram of a core assembly in an embodiment of the compressor of the present application.

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

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

[0045] Figure 5 is a sectional view of an embodiment of the self-adjusting oil pump system of the present application.

[0046] Figure 6 is a structural exploded view of a self-adjusting oil pump assembly in an embodiment of the self-adjusting oil pump system of the present application.

[0047] Figure 7 is a perspective view of a crankshaft in an embodiment of the self-adjusting oil pump system of the present application.

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

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

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

[0051] Figure 11 is a structural view of an oil guide member in an embodiment of the self-regulating oil pump system of the present invention.

[0052] Figure 12 is a sectional view of an oil guide member in an embodiment of the self-regulating oil pump system of the present invention.

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

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

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

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

[0057] Figure 17 is a state view of a sliding valve moving from a first working position to a second working position in an embodiment of the self-regulating oil pump system of the present invention.

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

[0059] The present invention will be further described with reference to the drawings and embodiments. DETAILED DESCRIPTION

[0060] Various exemplary embodiments of the present invention will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely meant to be illustrative and not limiting of the present invention. The present invention can be implemented in numerous different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and fully convey the scope of the present invention to those skilled in the art. It should be noted that relative arrangements of components and steps, components of materials, numerical expressions, and numerical values set forth in these embodiments are to be interpreted as merely exemplary, unless otherwise specifically stated.

[0061] The terms "first", "second", and similar terms in the present invention do not denote any order, quantity, or importance, but are used to distinguish different parts. The terms "include", "comprise", and similar terms mean that the elements before the terms encompass the elements listed after the terms, and do not exclude the possibility of also encompassing other elements. The terms "upper", "lower", "left", "right", and the like are used only to indicate relative positional relationships, and when the absolute positions of the described objects are changed, the relative positional relationships can also be changed 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 can be an intervening device between the specific device and the first device or the second device, or there can be no intervening device. When it is described that a specific device is connected to another device, the specific device can be directly connected to the other device without an intervening device, or can not be directly connected to the other device with an intervening device.

[0063] All terms used in the present invention, including technical terms or scientific terms, have the same meanings as those understood by a person of ordinary skill in the art, 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 art, and should not be interpreted in an idealized or extremely formalized sense, unless otherwise specifically defined herein.

[0064] Techniques, methods, and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered part of the specification where appropriate.

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

[0066] Referring to Figures 1 to 3 The compressor of the present embodiment includes a shell 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 exhaust 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 moves linearly in the cylinder of the cylinder block 211, thereby inhaling and compressing the refrigerant gas.

[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 immersed in the oil pool 300 of the compressor, thereby achieving the effect of pumping oil.

[0068] The crankshaft 3 comprises a long shaft 31, a crank 32 and a short shaft 33 connected in sequence, the long shaft 31 of the crankshaft 3 is rotationally matched with the shaft hole of the cylinder block 211, 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 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, 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] Referring to Figures 4 to 15 , the crankshaft 3 is provided with a first oil supply channel 34 and a second oil supply channel 35, the end of the long shaft 31 away from the short shaft 33 (i.e. the tail end of the crankshaft 3) is provided with a main oil gallery 36, the first oil supply channel 34 has a first oil inlet 341 and a first oil outlet 342, and the second oil supply channel 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 in communication with the main oil gallery 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 channel 35 comprises a first oil distribution gallery 353 and a second oil distribution gallery 354 connected in sequence, the main oil gallery 36, the first oil distribution gallery 353 and the second oil distribution gallery 354 are in communication in sequence and the inner diameters thereof decrease in sequence, the first oil distribution gallery 353 extends along the axial direction of the long shaft 31, and the second oil distribution gallery 354 is arranged obliquely relative to the axial direction of the long shaft 31. The first oil supply channel 34 comprises a first spiral oil distribution gallery 343, a third oil distribution gallery 344, a fourth oil distribution gallery 345, a fifth oil distribution gallery 346 and a second spiral oil distribution gallery 347 connected in sequence, the first spiral oil distribution gallery 343 extends spirally along the outer peripheral wall of the long shaft 31, the fourth oil distribution gallery 345 extends linearly and is arranged obliquely relative to the axial direction of the long shaft 31, the second spiral oil distribution gallery 347 extends spirally along the outer peripheral wall of the short shaft 33, and the first oil inlet 341 is located on the first spiral oil distribution gallery 343.

[0071] The self-adjusting oil pump assembly 4 is installed in the main oil gallery 36, and the self-adjusting oil pump assembly 4 comprises a sliding valve 41, a thermal sensing component 42, an oil guiding member 43, and a guide pipe 44, the sliding valve 41, the thermal sensing component 42, and the oil guiding member 43 are arranged in sequence along the axial direction of the long shaft 31, the guide pipe 44 is arranged in the main oil gallery 36 and is in interference fit with the main oil gallery 36, the oil guiding member 43 is installed in the guide pipe 44 and is in clearance fit with the guide pipe 44, the single-sided clearance between the oil guiding member 43 and the inner pipe wall 441 of the guide pipe 44 is 10-30 μm, the thermal sensing component 42 is located between the guide pipe 44 and the sliding valve 41, the first end of the thermal sensing component 42 is fixed between the guide pipe 44 by means of bonding, welding, or buckling, etc., and the second end of the thermal sensing component 42 is fixedly connected with the sliding valve 41 by means of bonding, welding, or buckling, etc.

[0072] Referring to Figure 5 , and Figures 13 to 15 , the sliding valve 41 is provided with a main oil hole 411, a first oil distribution hole 412, and a second oil distribution hole 413, the main oil hole 411 is recessed inward along the axial direction of the sliding valve 41 from the end close to the thermal sensing component 42, the first oil distribution hole 412 and the second oil distribution hole 413 are both in communication with the main oil gallery 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, and the secondary oil supply channel 35 is in communication 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 arranged at the end of the sliding valve 41 close to the second oil distribution hole 413.

[0073] The sliding valve 41 is further provided with an annular oil gallery 414, the annular oil gallery 414 is located on the 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 gallery 414, and the annular oil gallery 414 is in communication with the main oil hole 411 through the first oil distribution hole 412. The cross section of the annular oil gallery 414 is trapezoidal, and along the radial direction of the sliding valve 41, the width of the annular oil gallery 414 gradually increases from the bottom wall of the annular oil gallery 414 to the opening of the annular oil gallery 414.

[0074] The number, size and arrangement of the first oil distribution holes 412 and the second oil distribution holes 413 can be changed as needed. Preferably, the number of the first oil distribution holes 412 is two or more. In the present embodiment, the number of the first oil distribution holes 412 is four, and each first oil distribution hole 412 is arranged along the extension 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 greater 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 primary oil passage 34 in the second working position is greater than the amount of oil pumped into the primary oil passage 34 in the first working position. In other embodiments, the total cross-sectional area of each first oil distribution hole 412 does not necessarily have to be greater than the total cross-sectional area of each second oil distribution hole 413, as long as the amount of oil pumped into the primary oil passage 34 by the spool valve 41 in the second working position is greater than the amount of oil pumped into the primary oil passage 34 by the spool valve 41 in the first working position.

[0075] The main oil passage 36 and the first oil distribution passage 353 are connected to form a beveled step 37, and the end wall 410 of the spool valve 41 away from the heat-sensitive component 42 is tapered. The beveled step 37 is opposite to the tapered end wall 410 of the spool valve 41 and is limited and matched. Through the cooperation of the inclined angles of the two beveled surfaces, the adjustment of the oil discharge amount of the second oil distribution hole 413 is realized, and at the same time, the problem that the second oil distribution hole 413 is blocked and cannot pump oil to the secondary oil passage 35 when the spool valve 41 moves to the position abutting against the step is avoided.

[0076] The heat-sensitive component 42 is a heat-sensitive spring, and the base material of the heat-sensitive spring is a memory alloy. The Ac of the austenite of the memory alloy is greater than or equal to 65℃. The memory alloy is a binary memory alloy or a ternary memory alloy, and the memory alloy is a Ni-Ti memory alloy, a Cu-based memory alloy or a Fe-based memory alloy. The memory alloy has shape memory effect (SME) and superelasticity (SE). The shape memory effect (SME) refers to the ability of the memory alloy (SMAs) after cooling deformation to restore the original shape by heating, which is caused by reversible martensitic transformation. The superelasticity (SE) refers to the ability of the material to produce a strain far exceeding the elastic limit after plastic deformation, and the material can completely restore its original shape after the stress is removed. The Ac of the austenite of the memory alloy is within the operating temperature range of the compressor, and the actual operating temperature of the compressor is about room temperature to 200℃. When the temperature in the compressor is higher than the Ac of the austenite, the memory alloy gradually changes from the martensite phase to the austenite phase. When the temperature in the compressor is lower than the Ac of the austenite, the memory alloy gradually changes from the austenite phase to the martensite phase. By utilizing the reversible phase change of the microstructure of the memory alloy under temperature change, the deformation of the heat-sensitive component 42 is realized, and the movement of the spool valve 41 is further promoted. The stability is high, and no additional driving part is needed, which can reduce the cost.

[0077] The heat-sensitive component 42 can deform after being heated and drive the sliding valve 41 to move along the axial direction of the main oil passage 36 from the first working position to the second working position, and the heat-sensitive component 42 restores the shape after cooling and 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 first oil inlet port 341 is arranged in a staggered manner with the annular oil passage 414, the first oil inlet port 341 is not communicated with the first oil distribution hole 412, and the first oil inlet port 341 is located on the downstream side of the second oil distribution hole 413 along the flow direction of the lubricating oil. The first oil inlet port 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 is in abutment with the inclined step 37, the first oil inlet port 341 is arranged in a relative manner with the annular oil passage 414, the first oil inlet port 341 is located on the downstream side of the first oil distribution hole 412, and the first oil inlet port 341 is communicated with the main oil hole 411 through the first oil distribution hole 412.

[0080] The oil guiding part 43 is provided with a helical boss 430 extending along the outer peripheral wall of the oil guiding part 43 in a helical manner to form an oil guiding channel 431 extending along the outer peripheral wall of the oil guiding part 43 in a helical manner. The oil guiding channel 431 is communicated with the main oil passage 36, the oil guiding part 43 extends into the oil pool 300 and rotates with the crankshaft 3 to continuously transport the lubricating oil upward. The oil guiding part 43 is in a hollow structure and in a cylindrical shape, a hollow groove 432 is formed in the oil guiding part 43, the hollow groove 432 is recessed inward along the axial direction of the oil guiding part 43 from one end close to the heat-sensitive component 42. By arranging the oil guiding part 43 in a hollow structure, the weight of the overall structure can be reduced, and the cost can be reduced.

[0081] The self-adjusting oil pump system 5 further comprises a fixing frame 6, the fixing frame 6 is arranged at one end of the long shaft 31 away from the short shaft 33, and the oil guiding part 43 is fixedly connected with the fixing frame 6. Specifically, a fixing lug 433 is arranged on the bottom wall of the oil guiding part 43, a fixing hole 62 is arranged in the middle of the fixing frame 6, and a fixing pin 7 passes through the fixing lug 433 and the fixing hole 42 to fixedly connect the oil guiding part 43 with the fixing frame 6. The fixing frame 6 is further provided with a fixing portion 61, and the fixing portion 61 is used to be fixed with the shell of the motor assembly 220. The oil guiding part 43 is fixed and supported by the fixing frame 6, and the rotation of the oil guiding part 43 can be prevented.

[0082] The working method of the self-adjusting oil pump system 5 of the piston compressor for automatically adjusting the lubricating oil pump oil volume according to the operating condition of the compressor comprises the following steps:

[0083] Firstly, after the compressor is started, the lubricating oil at the bottom of the compressor is transported upward along the first oil inlet port 341 and the second oil inlet port 35 of the crankshaft 3 under the action of the oil guiding part 43 at the bottom end of the crankshaft 3 and the oil guiding pipe 44.

[0084] Referring to 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 in the high-frequency high-speed working condition, the oil temperature of the lubricating oil in the compressor also gradually increases. When the temperature exceeds the temperature 65℃ of the austenite start temperature line Ac of the memory alloy, the thermal induction spring of the memory alloy substrate starts to deform and elongate, driving the sliding valve 41 to move upward, so that the annular oil channel 414 corresponds to the first oil inlet 341, and the pump oil volume increases. At this time, it is in a gradual open flow state. As the compressor gradually operates in the low-frequency low-speed working condition, the oil temperature of the lubricating oil in the compressor also gradually decreases. When the temperature decreases below the temperature 65℃ of the austenite start temperature line Ac of the memory alloy, the thermal induction spring of the memory alloy substrate starts to recover and shorten, driving the sliding valve 41 to move downward, so that the first oil inlet 341 is misaligned with the annular oil channel 414, the first oil distribution hole 412 is not communicated with the first oil inlet 341, and the lubricating oil can only flow into the first oil inlet 341 through the second oil distribution hole 413, and the pump oil volume gradually decreases. At this time, it is in a gradual throttling state. That is, as the rotating speed of the crankshaft 3 increases or decreases, the temperature gradually increases or decreases, and the height of the sliding valve 41 increases or decreases, thereby enabling the self-adjusting pump oil system to automatically adjust the pump oil volume of the compressor according to the operating condition 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 also relatively high when the compressor operates at medium speed. However, when the compressor operates from low speed to medium speed, the oil temperature of the lubricating oil in the compressor exceeds the temperature 65℃ of the austenite start temperature line Ac of the memory alloy. When the temperature exceeds the temperature 65℃ of the austenite start temperature line Ac of the memory alloy, the thermal induction spring of the memory alloy substrate starts to deform and elongate, driving the sliding valve 41 to move upward, so that the annular oil channel 414 corresponds to the first oil inlet 341, and the pump oil volume increases. At this time, it is in a gradual open flow state. As the compressor gradually operates in the low-frequency low-speed working condition, the oil temperature of the lubricating oil in the compressor also gradually decreases. When the temperature decreases below the temperature 65℃ of the austenite start temperature line Ac of the memory alloy, the thermal induction spring of the memory alloy substrate starts to recover and shorten, driving the sliding valve 41 to move downward, so that the first oil inlet 341 is misaligned with the annular oil channel 414, the first oil distribution hole 412 is not communicated with the first oil inlet 341, and the lubricating oil can only flow into the first oil inlet 341 through the second oil distribution hole 413, and the pump oil volume gradually decreases. At this time, it is in a gradual throttling state. That is, as the rotating speed of the crankshaft 3 increases or decreases, the temperature gradually increases or decreases, and the height of the sliding valve 41 increases or decreases, thereby enabling the self-adjusting pump oil system to automatically adjust the pump oil volume of the compressor according to the operating condition of the compressor.

[0086] Meanwhile, with the height of the sliding valve 41 being raised or lowered, the cross-sectional area of the oil passage, through which the primary oil inlet 341 communicates with the annular oil gallery 414, is increased or decreased, so as to automatically adjust the size of the compressor pump oil according to the working pressure and operating conditions of the compressor.

[0087] As can be seen from the above, the self-adjusting oil pump system of the present application controls the movement of the sliding valve through the thermal induction structure to realize the movement of the sliding valve between the first working position and the second working position, thereby controlling the flow of lubricating oil entering the primary oil passage, so that the lubricating oil matches the working state. Since no additional unbalanced eccentric structure is added, the self-adjusting oil pump system does not generate additional unbalanced inertia force, and it can adjust the oil flow through the temperature in the cavity of the compressor. When the compressor is running in a high-frequency high-speed operating condition, the temperature in the compressor rises. When the working temperature exceeds the austenite starting temperature line of the thermal induction component, the self-adjusting oil pump of the present application starts to work, so that the primary oil inlet between the main oil gallery and the primary oil passage is opened. Since the total cross-sectional area of the first oil distribution hole is large, more oil is pumped out through the primary oil passage, thereby increasing the amount of lubricating oil at the gap between the connecting rod, the piston and the cylinder provided on the upper end of the crankshaft, thereby avoiding wear and failure of the crankshaft, the connecting rod, the piston and the cylinder, i.e. improving the pump oil amount of the compressor in high-frequency operating conditions, avoiding the problem of wear between parts due to the reduction of lubricating oil viscosity, and improving the oil film sealing performance between the piston and the cylinder, reducing leakage, and improving the refrigeration performance of the compressor in high-frequency operating conditions.

[0088] In addition, when the wide-frequency piston compressor is running in a high-pressure difference (△P is above 1.5 MPa) operating condition, even if the compressor is running at a medium or low speed in a medium or low operating condition, the temperature in the compressor will be relatively high at this time, especially the temperature in the medium-frequency operating condition will be much higher than that in the original medium-frequency operating condition with low pressure difference, thereby causing the viscosity of the lubricating oil in the compressor to decrease, so that a stable lubricating oil film cannot be formed between the parts to avoid wear of the parts, and the leakage problem between the piston and the cylinder is also avoided. Therefore, even if the compressor is in a medium or low frequency operating condition, the self-adjusting oil pump of the present application will work, and the problem of wear between parts due to the reduction of lubricating oil viscosity, which cannot form a stable oil film, is solved, the oil film sealing performance between the piston and the cylinder in medium and low frequency operating conditions is improved, the leakage is reduced, and the refrigeration performance of the compressor in medium and low frequency operating conditions is improved.

[0089] Meanwhile, since no additional unbalanced eccentric structure is added, the shaft balance structure of the original wide-frequency piston compressor pump body is not damaged, so that the friction power consumption, vibration and noise of the wide-frequency piston compressor are not increased, and the user experience is improved.

[0090] Finally, it should be noted that the above merely represents the preferred embodiments of the present application and is not intended to limit the present application, and the present application can have various changes and modifications for those skilled in the art, and any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. Self-regulating oil pump system, including crankshaft; The crankshaft includes a long shaft, a crank, and a short shaft connected in sequence. The crankshaft has a primary oil supply channel and a secondary oil supply channel. The end of the long shaft away from the short shaft has a main oil passage. The primary oil supply channel has a primary oil inlet and a primary oil outlet, and the secondary oil supply channel has a secondary oil inlet and a secondary oil outlet. Both the primary oil inlet and the secondary oil inlet are 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. Its features are: The self-regulating oil pump system also includes a self-regulating oil pump assembly, which is installed in the main oil passage; The self-regulating oil pump assembly includes a sliding valve, a heat-sensing component, and an oil priming component arranged sequentially 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 passage through the main oil hole. The second oil distribution hole is located on the end wall of the sliding valve away from the heat sensing component. The secondary oil supply channel is connected to 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. When heated, the heat-sensing component can deform and drive the sliding valve to move from the first working position to the second working position along the axial direction of the main oil passage. After the heat-sensing component cools down, it restores its shape and drives the sliding valve to reset. In the first working position, the primary oil inlet is connected to the main oil inlet 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 inlet through the first oil distribution hole; When the sliding valve is in the second working position, the amount of oil pumped into the primary oil supply channel is greater than the amount of oil pumped into the primary oil supply 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 to the main oil hole through the first oil distribution hole. When the sliding valve is in the first working position, the primary oil inlet is misaligned with the annular oil passage. When the sliding valve is in the second working position, the first-stage 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 passage is trapezoidal, and the width of the annular oil passage gradually increases from the bottom wall to the opening of the annular oil passage.

4. The self-regulating oil pump system according to claim 2, characterized in that: The number of the first oil distribution holes is two or more, and each of the first oil distribution holes is arranged along the extension 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 distribution hole is greater than the total cross-sectional area of ​​the second oil distribution hole.

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

7. The self-regulating oil pump system according to claim 6, characterized in 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.

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 also includes an oil guide pipe, which is disposed in the main oil passage and is interference-fitted with the main oil passage. The heat-sensing component is located between the oil guide pipe and the sliding valve, and the first end of the heat-sensing component is fixed to the oil guide pipe; The oil guide is installed inside the oil guide pipe and is fitted with the oil guide pipe with a clearance.

9. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The oil-drawing component has an oil-drawing channel that extends spirally along the outer peripheral wall of the oil-drawing component, and the oil-drawing channel is connected to 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-injecting component has a hollow structure.

11. The self-regulating oil pump system according to any one of claims 1 to 4, characterized in that: The self-adjusting oil pump system also includes a mounting bracket, which is disposed at the end of the long axis away from the short axis; The oil-drawing component is fixedly connected to the fixing frame, and the fixing frame is also provided with a fixing part.

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 inward from the end closest to the heat-sensing component along the axial direction of the sliding valve; The first oil distribution hole is located on the sliding valve at one end near 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 oil supply channel includes a first branch oil channel and a second branch oil channel connected to each other. The main oil channel, the first branch oil channel, and the second branch oil channel are sequentially connected and their inner diameters decrease sequentially. The first branch oil channel extends along the axial direction of the long axis, and the second branch oil channel is inclined relative to the axial direction of the long axis; and / or The primary oil supply channel includes a first spiral oil distribution channel, a third oil distribution channel, a fourth oil distribution channel, a fifth oil distribution channel, and a second spiral oil distribution channel connected in sequence. The first spiral oil distribution channel extends spirally along the outer peripheral wall of the long axis. The fourth oil distribution channel extends in a straight line and is inclined relative to the axial direction of the long axis. The second spiral oil distribution channel extends spirally along the outer peripheral wall of the short axis. The primary oil inlet is located on the first spiral oil distribution channel.

14. The self-regulating oil pump system according to claim 13, characterized in that: The connection between the main oil passage and the first branch oil passage forms a sloping step. The end wall of the sliding valve away from the heat-sensing component is conical. The sloping step is opposite to and limits the conical end wall of the sliding valve.

15. A compressor, characterized in that, Includes the self-regulating oil pump system as described in any one of claims 1 to 14.

16. A refrigeration device, characterized in that, Includes the compressor as described in claim 15.

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