CN204371594U - Linear compressor - Google Patents
Linear compressor Download PDFInfo
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- CN204371594U CN204371594U CN201420847662.8U CN201420847662U CN204371594U CN 204371594 U CN204371594 U CN 204371594U CN 201420847662 U CN201420847662 U CN 201420847662U CN 204371594 U CN204371594 U CN 204371594U
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Abstract
The utility model provides a kind of linear compressor, and linear compressor comprises: motor, comprises stator (31) and mover (32); Resonance mechanism, comprise multiple resonant springs (60) of the spring support (50) being connected to mover (32) and the side being at least arranged on spring support (50), between multiple circles at the two ends of resonant springs (60), equal gapless is arranged, and the end face at the two ends of resonant springs (60) all has flat surface grinding.The technical solution of the utility model efficiently solves the frictional loss of cylinder in prior art and larger problem of wearing and tearing.
Description
Technical field
The utility model relates to compression technique area, in particular to a kind of linear compressor.
Background technique
In prior art, as depicted in figs. 1 and 2, linear compressor comprises housing 1, cylinder 2, motor 3, piston 4, Aspirating valves 5a, outlet valve 5b, exhaust valve cap 5c, outlet pipe 5d, resonant springs 6a, exhaust valve spring 6b, supported spring 6c, fixed plate 7 and spring cup 8.After the coil of the motor 3 of linear compressor passes to electric current, the mover 3b forming closed alternation magnetic circuit drive motor 3 at the stator 3a of motor 3 moves, thus drives piston 4 reciprocating relative to cylinder 2, realizes the process of the suction of gas, compression and discharge.Gas is inhaled in housing 1 through the intakeport 1a of housing 1, low-pressure gas in housing 1 is inhaled into compressor chamber through Aspirating valves 5a, after gas in compressor chamber is compressed, when pressure reaches a timing, outlet valve 5b opens, the outlet pipe 5d of pressurized gas in housing 1, is discharged to outside the housing 1 of compressor.
Linear compressor needs to design a set of quality resonator system, and resonator system comprises resonant springs 6a, and resonant springs 6a is arranged between mover 3b and spring cup 8.The rigidity of resonant springs in resonator system in the moving direction of piston 4 is k
m, the gas equivalent stiffness in compression chamber is k
g, the static part quality being fixedly connected with 6a with cylinder 2 is m
s, static part comprises cylinder 2, mover 3b, fixed plate 7, outlet valve 5b, exhaust valve spring 6b and exhaust valve cap 5c, and the heavy moving parts be fixedly connected with piston 4 is m
d, moving element comprises piston 4 and mover 3b, resonant springs 6a equivalence is m to the quality on static part
ss, resonant springs 6a equivalence is m to heavy moving parts
sd.The resonator system natural frequency ω of linear compressor
n=[(k
m+ k
g) (m
s+ m
ss+ m
d+ m
sd)]/[(m
s+ m
ss) (m
d+ m
sd)], the design and operation frequencies omega of linear compressor and resonator system natural frequency ω
nunanimously, thus make compressor obtain most high energy efficiency, realize the resonance requirement of linear compressor.But, when piston 4 to-and-fro motion, resonant springs 6a can be extruded, because resonant springs 6a has elasticity, and the resonant springs 6a uneven possibility run-off the straight when being extruded, and then resonant springs 6a can produce lateral force, the lateral force of resonant springs 6a can produce active force to piston 4, thus makes the run-off the straight of piston possibility, and tilting of the piston can collide with cylinder, cause the frictional loss of cylinder and wearing and tearing comparatively large, reduce the efficiency of linear compressor.
Model utility content
Main purpose of the present utility model is to provide a kind of linear compressor, with the problem that the frictional loss and wearing and tearing that solve cylinder in prior art are larger.
To achieve these goals, the utility model provides a kind of linear compressor, it is characterized in that, comprising: motor, comprises stator and mover; Resonance mechanism, comprises multiple resonant springs of the spring support being connected to mover and the side being at least arranged on spring support, and between multiple circles at the two ends of resonant springs, equal gapless is arranged, and the end face at the two ends of resonant springs all has flat surface grinding.
Further, linear compressor also comprises cylinder, fixed plate and spring cup, fixed plate is arranged on stator, stator is between fixed plate and cylinder, spring cup lid is located on fixed plate, and the first end of resonant springs of the opposite side that the first end being positioned at the resonant springs of the side of spring support abuts with fixed plate and/or is positioned at spring support abuts with spring cup.
Further, resonant springs comprises the first resonant springs and the second resonant springs, first resonant springs is arranged on the first side of spring support, second resonant springs is arranged on the second side of spring support, the first end of the first resonant springs abuts with fixed plate, the first end of the second resonant springs abuts with spring cup, and the end face at the two ends of the first resonant springs all has the first flat surface grinding, and the end face at the two ends of the second resonant springs all has the second flat surface grinding.
Further, the first side of spring support is provided with the first boss, and the second end of the first resonant springs is arranged on the first boss, and the second side of spring support is provided with the second boss, and the second end of the second resonant springs is installed on the second boss.
Further, the number of the first resonant springs and the second resonant springs is even number.
Further, the circumferential size that the circumferential size of the first flat surface grinding accounts for the 1/2 ~ 7/8 of the circumferential size of the first resonant springs, second flat surface grinding accounts for 1/2 ~ 7/8 of the circumferential size of the second resonant springs.
Further, the center line along its length of spring support is X-axis, the axes intersect of X-axis and cylinder, the center line along its width direction of spring support is Y-axis, axis and the X-axis of Y-axis and cylinder are all crossing, multiple first resonant springs is relative to X-axis and the equal positional symmetry of Y-axis, and multiple second resonant springs is relative to X-axis and the equal positional symmetry of Y-axis.
Further, the rotation direction of a pair first resonant springs arranged in diagonal is contrary to the rotation direction of the first resonant springs with another setting in diagonal, and the rotation direction of a pair second resonant springs arranged in diagonal is contrary to the rotation direction of the second resonant springs with another setting in diagonal.
Further, the non-flat surface grinding of a pair first resonant springs arranged in diagonal is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, and the non-flat surface grinding of a pair second resonant springs arranged in diagonal is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis.
Further, the non-flat surface grinding of a pair first resonant springs arranged in right opposite is symmetrical arranged relative to X-axis or Y-axis, and the non-flat surface grinding of a pair second resonant springs arranged in right opposite is symmetrical arranged relative to X-axis or Y-axis.
Application the technical solution of the utility model, the end face at the two ends of resonant springs all has flat surface grinding, when piston reciprocating runs, resonant springs is extruded, the active force that flat surface grinding can make resonant springs be subject to more uniformly acts on miscellaneous part, effectively prevent the situation of run-off the straight when resonant springs is extruded, reduce or eliminate the lateral force of resonant springs, and then the impact that the lateral force reducing resonant springs coordinates with cylinder piston, efficiently avoid the situation of piston run-off the straight in the cylinder, thus ensure that the coaxality of piston and cylinder, reduce wear consumption and the wearing and tearing of cylinder, effectively improve the efficiency of linear compressor.Due to polish resonant springs end face after the intensity of resonant springs is reduced, multiple circles at the two ends of resonant springs are all close to setting, this enhance the intensity of resonant springs, thus it is more steady that piston is run in the cylinder, enhances the balance of piston.
Accompanying drawing explanation
The Figure of description forming a application's part is used to provide further understanding of the present utility model, and schematic description and description of the present utility model, for explaining the utility model, is not formed improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 shows the structural representation of the linear compressor of prior art;
Fig. 2 shows the structural representation of the resonant springs of the linear compressor of Fig. 1;
Fig. 3 shows the cylinder of Fig. 2 and the structural representation of piston;
Fig. 4 shows the inside perspective view of the embodiment according to linear compressor of the present utility model;
Fig. 5 shows the part-structure schematic diagram of the linear compressor of Fig. 4;
Fig. 6 shows the assembly structure schematic diagram of the spring support of the linear compressor of Fig. 4, mover and piston;
Fig. 7 shows the decomposition texture schematic diagram of the spring support of Fig. 6, mover and piston;
Fig. 8 shows the spring support of Fig. 4 and the structural representation of resonant springs;
Fig. 9 shows the schematic front view of first resonant springs of Fig. 8;
Figure 10 shows the spring support of Fig. 8 and the elevational schematic view of resonant springs;
The A-A of spring support and resonant springs that Figure 11 shows Figure 10 is to cross-sectional schematic;
Figure 12 shows the structural representation of the spring support of Fig. 8 and the assembling mode one of resonant springs;
Figure 13 shows the structural representation of the opposite side of the spring support of Figure 12 and the assembling mode one of resonant springs;
Figure 14 shows the structural representation of the spring support of Fig. 8 and the assembling mode two of resonant springs;
Figure 15 shows the structural representation of the opposite side of the spring support of Figure 14 and the assembling mode two of resonant springs;
Figure 16 shows the structural representation of the spring support of Fig. 8 and the assembling mode three of resonant springs;
Figure 17 shows the structural representation of the opposite side of the spring support of Figure 16 and the assembling mode three of resonant springs;
Figure 18 shows the structural representation of the spring support of Fig. 8 and the assembling mode four of resonant springs;
Figure 19 shows the structural representation of the opposite side of the spring support of Figure 18 and the assembling mode four of resonant springs;
Figure 20 shows the structural representation of the spring support of Fig. 8 and the assembling mode five of resonant springs;
Figure 21 shows the structural representation of the opposite side of the spring support of Figure 20 and the assembling mode five of resonant springs;
Figure 22 shows the structural representation of the spring support of Fig. 8 and the assembling mode six of resonant springs; And
Figure 23 shows the structural representation of the opposite side of the spring support of Figure 22 and the assembling mode six of resonant springs.
Wherein, above-mentioned accompanying drawing comprises the following drawings mark:
1, housing; 1a, intakeport; 1b, relief opening; 2, cylinder; 3, motor; 3a, stator; 3b, mover; 4, piston; 5a, Aspirating valves; 5b, outlet valve; 5c, exhaust valve cap; 5d, outlet pipe; 6a, resonant springs; 6b, exhaust valve spring; 6c, supported spring; 7, fixed plate; 8, spring cup; 20, cylinder; 31, stator; 32, mover; 321, the second positioning hole; 322, the second mounting hole; 40, piston; 41, the 3rd positioning hole; 42, the 3rd mounting hole; 50, spring support; 51, the first boss; 52, the second boss; 53, the first positioning hole; 54, the first mounting hole; 60, resonant springs; 61, the first resonant springs; 61a, the first left resonant springs; 61b, the second left resonant springs; 61c, the first right resonant springs; 61d, the second right resonant springs; 611, the first flat surface grinding; 62, the second resonant springs; 62a, first time resonant springs; Resonant springs on 62b, first; 62c, second time resonant springs; Resonant springs on 62d, second; 621, the second flat surface grinding; 70, fixed plate; 71, the 3rd boss; 80, spring cup; 90, the first fastening piece.
Embodiment
It should be noted that, when not conflicting, the embodiment in the application and the feature in embodiment can combine mutually.Below with reference to the accompanying drawings and describe the utility model in detail in conjunction with the embodiments.
As shown in figs. 4 and 7, the linear compressor of the present embodiment comprises housing, cylinder 20, motor, piston 40, resonance mechanism, housing has inner chamber, cylinder 20 is installed in the lumen, cylinder 20 has compression chamber, motor is installed in the lumen and is connected with cylinder 20, motor comprises stator 31 and mover 32, the first end of piston 40 is arranged in compression chamber movably, second end of piston 40 stretches out compression chamber and is connected with mover 32, resonance mechanism comprises multiple resonant springs 60 of the spring support 50 being connected to mover 32 and the both sides being arranged on spring support 50, between multiple circles at the two ends of resonant springs 60, equal gapless is arranged, the end face at the two ends of resonant springs 60 all has flat surface grinding.
The linear compressor of application the present embodiment, the end face at the two ends of resonant springs 60 all has flat surface grinding, when piston 40 is toward when running, resonant springs 60 is extruded, the active force that flat surface grinding can make resonant springs 60 be subject to more uniformly acts on miscellaneous part, effectively prevent the situation of run-off the straight when resonant springs 60 is extruded, reduce or eliminate the lateral force of resonant springs 60, and then the impact that the lateral force reducing resonant springs 60 coordinates with cylinder 20 piston 40, efficiently avoid the situation of piston 40 run-off the straight in cylinder 20, thus ensure that the coaxality of piston 40 and cylinder 20, reduce wear consumption and the wearing and tearing of cylinder 20, effectively improve the efficiency of linear compressor.Due to polish resonant springs 60 end face after the intensity of resonant springs 60 is reduced, multiple circles at the two ends of resonant springs 60 are all close to setting, this enhance the intensity of resonant springs 60, thus it is more steady that piston 40 is run in cylinder 20, enhances the balance of piston 40.
In the present embodiment, linear compressor also comprises fixed plate 70 and spring cup 80, fixed plate 70 is arranged on stator 31, stator 31 is between fixed plate 70 and cylinder 20, spring cup 80 lid is located on fixed plate 70, and the first end of resonant springs 60 of the opposite side that the first end being positioned at the resonant springs 60 of the side of spring support 50 abuts with fixed plate 70 and is positioned at spring support 50 abuts with spring cup 80.Spring support 50 can conveniently fix resonant springs 60, and the first end that fixed plate 70 and spring cup 80 are resonant springs 60 provides a yielding support point.Be fixed on stator 31 by fixed plate 70, spring cup 80 and spring support 50 like this.During installation, first by after resonant springs 60 precompression certain length, by screw, spring cup 80 is fixed on fixed plate 70.
As shown in Figure 7, in the present embodiment, spring support 50 is provided with the first positioning hole 53 and the first mounting hole 54, mover 32 is provided with the second positioning hole 321 and the second mounting hole 322, piston 40 be provided with the 3rd positioning hole 41 and the 3rd mounting hole 42, first fastening piece 90 successively through the first mounting hole 54, second mounting hole 322 and the 3rd mounting hole 42 so that piston 40, mover 32 and spring support 50 are fixed together in order.Preferably, the first fastening piece 90 is screw, and spring support 50 and mover 32 are fixed on piston 40 by screw.
In the present embodiment, fixed plate 70 is fixed on stator 31 by fastening piece.Preferably, fastening piece is screw, and the structure of screw is simple, easy to use, simple installation, rapid operation.
In prior art as shown in Figure 3, piston 4 tilts in cylinder 2, has angle d between the cylindrical axis of piston 4 and the inner circle axis of cylinder 2, and angle d crosses at tilt angle the inordinate wear that conference causes between piston 4 and cylinder 2.
For the problems referred to above, in the present embodiment, as shown in Figure 8 and Figure 9, resonant springs 60 comprises the first resonant springs 61 and the second resonant springs 62, first resonant springs 61 is arranged on the first side of spring support 50, second resonant springs 62 is arranged on the second side of spring support 50, the first end of the first resonant springs 61 abuts with fixed plate 70, the first end of the second resonant springs 62 abuts with spring cup 80, the end face at the two ends of the first resonant springs 61 all has the first flat surface grinding 611 (shadow region as Figure 12), the end face at the two ends of the second resonant springs 62 all has the second flat surface grinding 621 (as shown in figure 13).The active force that first flat surface grinding 611 can make the first resonant springs 61 be subject to more uniformly acts on fixed plate 70, effectively prevent the situation of run-off the straight when the first resonant springs 61 is extruded, reduce or eliminate the lateral force of the first resonant springs 61, and then the impact that the lateral force reducing the first resonant springs 61 coordinates with cylinder 20 piston 40, efficiently avoid the situation of piston 40 run-off the straight in cylinder 20, thus ensure that the coaxality of piston 40 and cylinder 20.The active force that second flat surface grinding 621 can make the second resonant springs 62 be subject to more uniformly acts on spring cup 80, effectively prevent the situation of run-off the straight when the second resonant springs 62 is extruded, reduce or eliminate the lateral force of the second resonant springs 62, and then the impact that the lateral force reducing the second resonant springs 62 coordinates with cylinder 20 piston 40, efficiently avoid the situation of piston 40 run-off the straight in cylinder 20, thus ensure that the coaxality of piston 40 and cylinder 20.By all arranging resonant springs in the both sides of spring support 50, in the suction of gas, compression and discharge process, more effectively reduce or eliminate the lateral force of resonant springs.
As shown in Fig. 6, Fig. 8 and Figure 11, in the present embodiment, first side of spring support 50 is provided with the first boss 51, second end of the first resonant springs 61 is arranged on the first boss 51, the second end that second side of spring support 50 is provided with the second boss 52, second resonant springs 62 is installed on the second boss 52.On the traffic direction of piston 40 relative to cylinder 20, establish elastic support (i.e. resonant springs 60) like this, the rigidity of elastic support is k
m.First boss 51 can facilitate the installation of the first resonant springs 61, and the second boss 52 can facilitate the installation of the second resonant springs 62, installs easier, easy to operate.Preferably, the second end of the first resonant springs 61 and the first boss 51 interference fit, the second end of the second resonant springs 62 and the second boss 52 interference fit.
As shown in Figure 5, in the present embodiment, fixed plate 70 is provided with first end and the 3rd boss 71 Spielpassung of the 3rd boss 71, first resonant springs 61, and spring cup 80 is provided with the 4th boss, the first end of the second resonant springs 62 and the 4th boss Spielpassung.
As shown in figs, in the present embodiment, the number of the first resonant springs 61 and the second resonant springs 62 is even number.The size of single resonant springs diminishes, and wire diameter and the stiffness coefficient of resonant springs easily ensure, reduce manufacturing cost.Preferably, the center line along its length of spring support 50 is X-axis, the axes intersect of X-axis and cylinder 20, the center line along its width direction of spring support 50 is Y-axis, axis and the X-axis of Y-axis and cylinder 20 are all crossing, multiple first resonant springs 61 is relative to X-axis and the equal positional symmetry of Y-axis, and multiple second resonant springs 62 is relative to X-axis and the equal positional symmetry of Y-axis.All resonant springs can be provided with like this on the length direction of spring support 50 and width direction, the impact that the lateral force effectively reducing resonant springs coordinates piston and cylinder, have effectively achieved compressor operating efficiency consistent with resonator system frequency, thus effectively improve the efficiency of compressor.Preferably, the first resonant springs 61 is four, and the second resonant springs 62 is four.Make structure simple like this, arrange easy, Be very effective.First resonant springs 61 comprises the first left resonant springs 61a, the second left resonant springs 61b, the first right resonant springs 61c and the second right resonant springs 61d, and the second resonant springs 61 to comprise on first time resonant springs 62a, first resonant springs 62d on resonant springs 62b, second time resonant springs 62c and second.Wherein, left and right and the upper and lower left and right referred in figure.
As shown in Figure 10, in the present embodiment, angle between the circle center line connecting of first boss 51 arranged in diagonal of the first side of spring support 50 and X-axis is a, between the circle center line connecting of second boss 52 arranged in diagonal of the second side of spring support 50 and Y-axis is b, wherein, the scope of b-a is in the scope of 0 ~ 20 °.Certainly, also can according to the scope of the size design b-a of concrete compressor.
In the present embodiment, the circumferential size that the circumferential size of the first flat surface grinding 611 accounts for the 1/2 ~ 7/8, second flat surface grinding 621 of the circumferential size of the first resonant springs 61 accounts for 1/2 ~ 7/8 of the circumferential size of the second resonant springs 62.In prior art, as shown in Figure 2, the end face position of resonant springs polishes, then resonant springs is mated the contact area of part is not plane contact, after resonant springs precompression, the direction of the compressive force of resonant springs and the axial direction of resonant springs not in the same way, namely have angle c between the direction of the compressive force of resonant springs and the axial direction of resonant springs.And in the present embodiment, as shown in Figure 9, the two ends of the first resonant springs 61 and the second resonant springs 62 all polish, tightly to arrange between the circle that the tail circle at the two ends of the first resonant springs 61 and the second resonant springs 62 is adjacent, can ensure that resonant springs is mated between part and form effective fitting surface, reduce the deviation angle of the direction of the compressive force of single resonant springs and the axial direction of resonant springs, thus the lateral force that reduction single-piece spring pre-compression force produces.
In the present embodiment, spring support 50 is several as follows with the assembling mode of resonant springs 60:
1) rotation direction of four the first resonant springs 61 is all identical, and the rotation direction of four the second resonant springs 62 is all identical, and the rotation direction of the first resonant springs 61 is identical with the rotation direction of the second resonant springs 62.If the first resonant springs 61 and the second resonant springs 62 are dextrorotation spring, at this moment the first resonant springs 61, second resonant springs 62 has following three kinds of assembling modes with spring support 50:
The first assembling mode is: close together and the non-flat surface grinding of a pair first resonant springs 61 arranged in right opposite are symmetrical arranged relative to X-axis, and close together and the non-flat surface grinding of a pair second resonant springs 62 arranged in right opposite are symmetrical arranged relative to Y-axis.Particularly, the non-flat surface grinding of the first left resonant springs 61a and the non-flat surface grinding of the second left resonant springs 61b are symmetrical arranged relative to X-axis, the non-flat surface grinding of the first right resonant springs 61c and the non-flat surface grinding of the second right resonant springs 61d are symmetrical arranged relative to X-axis, the non-flat surface grinding of the non-flat surface grinding of first time resonant springs 62a and second time resonant springs 62c is symmetrical arranged relative to Y-axis, on first resonant springs 62b non-flat surface grinding and second on the non-flat surface grinding of resonant springs 62d be symmetrical arranged relative to Y-axis.Be direction in opposite directions as shown in Figure 12 and Figure 13, its direction also can for supporting or opposing certainly.
The lateral force of the first left resonant springs 61a and the lateral force of the second left resonant springs 61b balance mutually, the lateral force of the first right resonant springs 61c and the lateral force of the second right resonant springs 61d balance mutually, the lateral force of the lateral force of first time resonant springs 62a and second time resonant springs 62c balances mutually, on first resonant springs 62b lateral force and second on the lateral force of resonant springs 62d mutually balance, thus eliminate assembly spring lateral force, spring lateral force is avoided to destroy the precision-fit of piston and cylinder, avoid the excessive friction power loss between piston and cylinder and inordinate wear.
The second assembling mode is: the non-flat surface grinding of a pair first resonant springs 61 arranged in diagonal is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, and the non-flat surface grinding of a pair second resonant springs 62 arranged in diagonal is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis.Particularly, the non-flat surface grinding of the first left resonant springs 61a and the non-flat surface grinding of the second right resonant springs 61d are arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, the non-flat surface grinding of the second left resonant springs 61b and the non-flat surface grinding of the first right resonant springs 61c are arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, on the non-flat surface grinding of first time resonant springs 62a and second, the non-flat surface grinding of resonant springs 62d is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, on first, the non-flat surface grinding of resonant springs 62b and the non-flat surface grinding of second time resonant springs 62c are arranged relative to the intersection point Central Symmetry of X-axis and Y-axis.Be direction in opposite directions as shown in Figure 14 and Figure 15, its direction also can for supporting or opposing certainly.
The lateral force of the first left resonant springs 61a and the lateral force of the second right resonant springs 61d balance mutually, the lateral force of the second left resonant springs 61b and the lateral force of the first right resonant springs 61c balance mutually, in the lateral force of first time resonant springs 62a and second, the lateral force of resonant springs 62d balances mutually, on first, the lateral force of resonant springs 62b and the lateral force of second time resonant springs 62c balance mutually, thus eliminate assembly spring lateral force, spring lateral force is avoided to destroy the precision-fit of piston and cylinder, avoid the excessive friction power loss between piston and cylinder and inordinate wear.
The third assembling mode is: distant and non-flat surface grinding that is a pair first resonant springs 61 that are that arrange in right opposite is symmetrical arranged relative to Y-axis, and distant and non-flat surface grinding that is a pair second resonant springs 62 that are that arrange in right opposite is symmetrical arranged relative to X-axis.Particularly, the non-flat surface grinding of the first left resonant springs 61a and the non-flat surface grinding of the first right resonant springs 61c are symmetrical arranged relative to Y-axis, the non-flat surface grinding of the second left resonant springs 61b and the non-flat surface grinding of the second right resonant springs 61d are symmetrical arranged relative to Y-axis, on the non-flat surface grinding of first time resonant springs 62a and first, the non-flat surface grinding of resonant springs 62b is symmetrical arranged relative to X-axis, and on the non-flat surface grinding of second time resonant springs 62c and second, the non-flat surface grinding of resonant springs 62d is symmetrical arranged relative to X-axis.Be direction in opposite directions as shown in Figure 16 and Figure 17, its direction also can for supporting or opposing certainly.
The lateral force of the first left resonant springs 61a and the lateral force of the first right resonant springs 61c balance mutually, the lateral force of the second left resonant springs 61b and the lateral force of the second right resonant springs 61d balance mutually, in the lateral force of first time resonant springs 62a and first, the lateral force of resonant springs 62b balances mutually, in the lateral force of second time resonant springs 62c and second, the lateral force of resonant springs 62d balances mutually, thus eliminate assembly spring lateral force, spring lateral force is avoided to destroy the precision-fit of piston and cylinder, avoid the excessive friction power loss between piston and cylinder and inordinate wear.
2) rotation direction of a pair first resonant springs 61 arranged in diagonal is contrary to the rotation direction of the first resonant springs 61 with another setting in diagonal, and the rotation direction of a pair second resonant springs 62 arranged in diagonal is contrary to the rotation direction of the second resonant springs 62 with another setting in diagonal.If in diagonal arrange a pair first resonant springs 61 and in diagonal arrange a pair second resonant springs 62 be dextrorotation spring, in diagonal arrange another to the first resonant springs 61 and in diagonal arrange another left-handed spring is to the second resonant springs 62.Particularly, on first left resonant springs 61a, the second right resonant springs 61d, first, resonant springs 62b and second time resonant springs 62c is dextrorotation spring, on second left resonant springs 61b, the first right resonant springs 61c, first time resonant springs 62a and second, resonant springs 62d is left-handed spring, and at this moment the first resonant springs 61, second resonant springs 62 has following three kinds of assembling modes with spring support 50:
The first assembling mode is: close together and the non-flat surface grinding of a pair first resonant springs 61 arranged in right opposite are symmetrical arranged relative to X-axis, and close together and the non-flat surface grinding of a pair second resonant springs 62 arranged in right opposite are symmetrical arranged relative to Y-axis.Particularly, the non-flat surface grinding of the first left resonant springs 61a and the non-flat surface grinding of the second left resonant springs 61b are symmetrical arranged relative to X-axis, the non-flat surface grinding of the first right resonant springs 61c and the non-flat surface grinding of the second right resonant springs 61d are symmetrical arranged relative to X-axis, the non-flat surface grinding of the non-flat surface grinding of first time resonant springs 62a and second time resonant springs 62c is symmetrical arranged relative to Y-axis, on first resonant springs 62b non-flat surface grinding and second on the non-flat surface grinding of resonant springs 62d be symmetrical arranged relative to Y-axis.Be direction in opposite directions as shown in Figure 18 and Figure 19, its direction also can for supporting or opposing certainly.
The lateral force of the first left resonant springs 61a and the lateral force of the second left resonant springs 61b balance mutually, and the lateral force of the first right resonant springs 61c and the lateral force of the second right resonant springs 61d balance mutually, and circumferential moment of torsion balances mutually; The lateral force of the lateral force of first time resonant springs 62a and second time resonant springs 62c balances mutually, on first resonant springs 62b lateral force and second on the lateral force of resonant springs 62d mutually balance, circumferential moment of torsion balances mutually; Thus eliminate assembly spring lateral force, avoid spring lateral force to destroy the precision-fit of piston and cylinder, avoid the excessive friction power loss between piston and cylinder and inordinate wear.
The second assembling mode is: the non-flat surface grinding of a pair first resonant springs 61 arranged in diagonal is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, and the non-flat surface grinding of a pair second resonant springs 62 arranged in diagonal is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis.Particularly, the non-flat surface grinding of the first left resonant springs 61a and the non-flat surface grinding of the second right resonant springs 61d are arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, the non-flat surface grinding of the second left resonant springs 61b and the non-flat surface grinding of the first right resonant springs 61c are arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, on the non-flat surface grinding of first time resonant springs 62a and second, the non-flat surface grinding of resonant springs 62d is arranged relative to the intersection point Central Symmetry of X-axis and Y-axis, on first, the non-flat surface grinding of resonant springs 62b and the non-flat surface grinding of second time resonant springs 62c are arranged relative to the intersection point Central Symmetry of X-axis and Y-axis.Be direction in opposite directions as shown in Figure 20 and Figure 21, its direction also can for supporting or opposing certainly.
The lateral force of the first left resonant springs 61a and the lateral force of the second right resonant springs 61d balance mutually, and the lateral force of the second left resonant springs 61b and the lateral force of the first right resonant springs 61c balance mutually, and circumferential moment of torsion balances mutually; In the lateral force of first time resonant springs 62a and second, the lateral force of resonant springs 62d balances mutually, and on first, the lateral force of resonant springs 62b and the lateral force of second time resonant springs 62c balance mutually, and circumferential moment of torsion balances mutually; Thus eliminate assembly spring lateral force, avoid spring lateral force to destroy the precision-fit of piston and cylinder, avoid the excessive friction power loss between piston and cylinder and inordinate wear.
The third assembling mode is: distant and non-flat surface grinding that is a pair first resonant springs 61 that are that arrange in right opposite is symmetrical arranged relative to Y-axis, and distant and non-flat surface grinding that is a pair second resonant springs 62 that are that arrange in right opposite is symmetrical arranged relative to X-axis.Particularly, the non-flat surface grinding of the first left resonant springs 61a and the non-flat surface grinding of the first right resonant springs 61c are symmetrical arranged relative to Y-axis, the non-flat surface grinding of the second left resonant springs 61b and the non-flat surface grinding of the second right resonant springs 61d are symmetrical arranged relative to Y-axis, on the non-flat surface grinding of first time resonant springs 62a and first, the non-flat surface grinding of resonant springs 62b is symmetrical arranged relative to X-axis, and on the non-flat surface grinding of second time resonant springs 62c and second, the non-flat surface grinding of resonant springs 62d is symmetrical arranged relative to X-axis.Be direction in opposite directions as shown in Figure 22 and Figure 23, its direction also can for supporting or opposing certainly.
The lateral force of the first left resonant springs 61a and the lateral force of the first right resonant springs 61c balance mutually, and the lateral force of the second left resonant springs 61b and the lateral force of the second right resonant springs 61d balance mutually, and circumferential moment of torsion balances mutually; In the lateral force of first time resonant springs 62a and first, the lateral force of resonant springs 62b balances mutually, and in the lateral force of second time resonant springs 62c and second, the lateral force of resonant springs 62d balances mutually, and circumferential moment of torsion balances mutually; Thus eliminate assembly spring lateral force, avoid spring lateral force to destroy the precision-fit of piston and cylinder, avoid the excessive friction power loss between piston and cylinder and inordinate wear.
The foregoing is only preferred embodiment of the present utility model, be not limited to the utility model, for a person skilled in the art, the utility model can have various modifications and variations.All within spirit of the present utility model and principle, any amendment done, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
Claims (10)
1. a linear compressor, is characterized in that, comprising:
Motor, comprises stator (31) and mover (32);
Resonance mechanism, comprise multiple resonant springs (60) of the spring support (50) being connected to described mover (32) and the side being at least arranged on described spring support (50), between multiple circles at the two ends of described resonant springs (60), equal gapless is arranged, and the end face at the two ends of described resonant springs (60) all has flat surface grinding.
2. linear compressor according to claim 1, it is characterized in that, described linear compressor also comprises cylinder (20), fixed plate (70) and spring cup (80), described fixed plate (70) is arranged on described stator (31), described stator (31) is positioned between described fixed plate (70) and described cylinder (20), described spring cup (80) lid is located on described fixed plate (70), the first end of described resonant springs (60) of the opposite side that the first end being positioned at the described resonant springs (60) of the side of described spring support (50) abuts with described fixed plate (70) and/or is positioned at described spring support (50) abuts with described spring cup (80).
3. linear compressor according to claim 2, it is characterized in that, described resonant springs (60) comprises the first resonant springs (61) and the second resonant springs (62), described first resonant springs (61) is arranged on the first side of described spring support (50), described second resonant springs (62) is arranged on the second side of described spring support (50), the first end of described first resonant springs (61) abuts with described fixed plate (70), the first end of described second resonant springs (62) abuts with described spring cup (80), the end face at the two ends of described first resonant springs (61) all has the first flat surface grinding (611), the end face at the two ends of described second resonant springs (62) all has the second flat surface grinding (621).
4. linear compressor according to claim 3, it is characterized in that, first side of described spring support (50) is provided with the first boss (51), second end of described first resonant springs (61) is arranged on described first boss (51), second side of described spring support (50) is provided with the second boss (52), and the second end of described second resonant springs (62) is installed on described second boss (52).
5. linear compressor according to claim 3, is characterized in that, the number of described first resonant springs (61) and described second resonant springs (62) is even number.
6. linear compressor according to claim 3, it is characterized in that, the circumferential size of described first flat surface grinding (611) accounts for 1/2 ~ 7/8 of the circumferential size of described first resonant springs (61), and the circumferential size of described second flat surface grinding (621) accounts for 1/2 ~ 7/8 of the circumferential size of described second resonant springs (62).
7. linear compressor according to claim 6, it is characterized in that, the center line along its length of described spring support (50) is X-axis, the axes intersect of described X-axis and described cylinder (20), the center line along its width direction of described spring support (50) is Y-axis, axis and the described X-axis of described Y-axis and described cylinder (20) are all crossing, multiple described first resonant springs (61) is relative to described X-axis and the equal positional symmetry of described Y-axis, multiple described second resonant springs (62) is relative to described X-axis and the equal positional symmetry of described Y-axis.
8. linear compressor according to claim 7, it is characterized in that, the rotation direction of the first resonant springs (61) described in a pair that arranges in diagonal is contrary to the rotation direction of described first resonant springs (61) with another setting in diagonal, and described in a pair that arranges in diagonal, the rotation direction of the second resonant springs (62) is contrary to the rotation direction of described second resonant springs (62) with another setting in diagonal.
9. linear compressor according to claim 8, it is characterized in that, the non-flat surface grinding of the first resonant springs (61) described in a pair that arranges in diagonal is arranged relative to the intersection point Central Symmetry of described X-axis and described Y-axis, and the non-flat surface grinding of the second resonant springs (62) described in a pair that arranges in diagonal is arranged relative to the intersection point Central Symmetry of described X-axis and described Y-axis.
10. linear compressor according to claim 8, it is characterized in that, described in a pair that arranges in right opposite, the non-flat surface grinding of the first resonant springs (61) is symmetrical arranged relative to described X-axis or described Y-axis, and described in a pair that arranges in right opposite, the non-flat surface grinding of the second resonant springs (62) is symmetrical arranged relative to described X-axis or described Y-axis.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420847662.8U CN204371594U (en) | 2014-12-25 | 2014-12-25 | Linear compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420847662.8U CN204371594U (en) | 2014-12-25 | 2014-12-25 | Linear compressor |
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| Publication Number | Publication Date |
|---|---|
| CN204371594U true CN204371594U (en) | 2015-06-03 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420847662.8U Expired - Fee Related CN204371594U (en) | 2014-12-25 | 2014-12-25 | Linear compressor |
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| CN (1) | CN204371594U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105781930A (en) * | 2014-12-25 | 2016-07-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Linear compressor |
| CN106704147A (en) * | 2015-08-18 | 2017-05-24 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body assembly, linear compressor, refrigeration system and heat pump system |
-
2014
- 2014-12-25 CN CN201420847662.8U patent/CN204371594U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105781930A (en) * | 2014-12-25 | 2016-07-20 | 珠海格力节能环保制冷技术研究中心有限公司 | Linear compressor |
| CN106704147A (en) * | 2015-08-18 | 2017-05-24 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body assembly, linear compressor, refrigeration system and heat pump system |
| CN106704147B (en) * | 2015-08-18 | 2019-05-31 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly, straight-line compressor, refrigeration system and heat pump system |
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Granted publication date: 20150603 Termination date: 20211225 |