JP2017155628A - Compressor and refrigerator with this compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor of which size can be made small while its poor operation is being prevented and to provide a refrigerator with this compressor.SOLUTION: A compression element 20 comprises a cylinder 21; a piston 22 for compressing refrigerant while being reciprocated in the cylinder 21; a crank shaft 23 eccentrically rotated by an electric element 30; a connecting rod 25 for rotatably connecting an eccentric part 23p of the crank shaft 23 with the piston 22; a piston pin 29 for rotatably connecting the piston 22 with the connecting rod 25; a radial bearing 26 for pivotally supporting the crank shaft 23. When a length in an axial length from an upper end of a main axis of the crank shaft to a lower end of the bearing is defined as L, and a pitch of a distance connecting a center of rotation of a small end part 25a of the connecting rod 25 with a center of rotation of a large end part 25b is defined as P, L/P is 1.1 or less.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor and a refrigerator including the compressor.

  A reciprocating compressor has a mechanism for compressing refrigerant by reciprocating a piston by rotating a crankshaft eccentrically with the power of an electric motor (see Patent Document 1).

JP 2010-281299 A

  By the way, in a reciprocating compressor, geometrical intersections such as squareness and parallelism as well as roundness and cylindricity of each sliding part are important. However, in the compressor described in Patent Document 1, when the crankshaft is shortened in order to reduce the size of the compressor, a load acting on the crankshaft increases due to an increase in the inclination of the crankshaft, resulting in a geometric tolerance. When the accuracy is low, the crankshaft eventually locks and the compressor does not operate normally.

  The present invention solves the above-mentioned conventional problems, and an object of the present invention is to provide a compressor that can be downsized while preventing malfunction and a refrigerator including the compressor.

  The present invention provides a compressor including a compression element, an electric element that drives the compression element, and a container that accommodates the compression element and the electric element. The compression element reciprocates in the cylinder. A piston that compresses the refrigerant by moving; a crankshaft that rotates eccentrically by the electric element; a rod that rotatably connects the eccentric portion of the crankshaft and the piston; and a bearing that supports the crankshaft; When the length in the axial direction from the upper end of the main shaft of the crankshaft to the lower end of the bearing is L, and the distance connecting the rotation center of one end of the rod and the rotation center of the other end is P, L / P is 1.1 or less.

  ADVANTAGE OF THE INVENTION According to this invention, the compressor which can be reduced in size while preventing a malfunction and a refrigerator provided with the same can be provided.

It is a longitudinal cross-sectional view which shows the compressor of this embodiment. It is a transverse cross section showing the compressor of this embodiment. It is explanatory drawing which shows the position dimension of each inclination angle by the clearance at the time of calculating | requiring the interference rate in a compressor. It is a graph which shows the relationship between an interference factor and COP. It is a graph which shows the relationship between an interference factor and spindle length / rod pitch. The schematic sectional drawing of the refrigerator carrying the compressor of this embodiment is shown, (a) is the structure which has arrange | positioned the compressor to the lower part, (b) is the structure which has arrange | positioned the compressor to the upper part.

Hereinafter, a compressor 100 according to an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a compressor of the present embodiment.
As shown in FIG. 1, the compressor 100 is a so-called reciprocating compressor configured by arranging a compression element 20 and an electric element 30 in a sealed container 3. The compression element 20 and the electric element 30 are elastically supported in the sealed container 3 via a plurality of coil springs 9 (elastic members). In the sealed container 3, an upper case 3 m that constitutes a substantially upper half outline and a lower case 3 n that constitutes a substantially lower half outline are joined by welding or the like, and a space for accommodating the compression element 20 and the electric element 30 is contained therein. Have.

  The compression element 20 includes a cylinder 21, a piston 22 that compresses refrigerant by reciprocating in the cylinder 21, a crankshaft 23 (crankshaft) that rotates eccentrically by the electric element 30, and an eccentric portion 23p of the crankshaft 23. And a connecting rod 25 (rod) for connecting the piston 22 and a radial bearing 26 (bearing) and a thrust bearing 27 (bearing) for supporting the crankshaft 23.

  The cylinder 21 is formed at an offset position on the outer side in the radial direction from the central axis O of the crankshaft 23 (main shaft 23a). The axial direction O1 of the cylinder 21 is configured to be orthogonal to the axial direction (center axis O) of the crankshaft 23. Further, a head cover 28 is attached to the outer peripheral end of the cylinder 21 in the axial direction O1, and a piston 22 is inserted into the opposite end. Thus, the compression chamber (cylinder chamber) Q1 is configured by the cylinder 21, the piston 22, and the head cover 28. Between the cylinder 21 and the head cover 28, a valve opening / closing mechanism (not shown) having an intake valve that opens when the refrigerant is sucked and a discharge valve that opens when the compressed refrigerant is discharged is provided.

  The piston 22 is connected to a small end portion 25 a (an end portion on the piston 22 side) of the connecting rod 25 via a piston pin 29. That is, the piston 22 is formed with a connecting hole 22a penetrating in the vertical direction and a recess 22b into which the small end 25a of the connecting rod 25 is inserted.

  The crankshaft 23 includes a main shaft 23a, a flange portion 23b that protrudes in the radial direction at the upper end of the main shaft 23a, and an eccentric portion 23p that is formed at a position eccentric from the central axis O of the main shaft 23a. . The center axis O of the main shaft 23a is set to be parallel to the rotation center axis of the eccentric portion 23p. Further, the lower end portion of the crankshaft 23 extends to the vicinity of the lower case 3n. The eccentric portion 23p rotates eccentrically with respect to the central axis O, so that the piston 22 reciprocates in the cylinder 21.

  The main shaft 23a has a cylindrical shape extending in the vertical direction, and is rotatably supported by a radial bearing 26. Further, the central axis O (axial direction) of the main shaft 23 a is configured to be parallel to the axial direction of the radial bearing 26.

  The flange portion 23b has a structure also used as a balance weight. The balance weight has a function of reducing vibration when the compression element 20 is driven. Thus, the balance weight is positioned between the main shaft 23a and the eccentric portion 23p, so that the height dimension of the compression element 20 can be reduced and the compressor 100 can be reduced in size.

  Further, the main shaft 23a of the crankshaft 23 is formed with a concave center hole 23c upward from the lower end surface in the axial direction, and has a hollow portion in the main shaft 23a. The crankshaft 23 is formed with an upper communication hole 23d penetrating from the upper end of the center hole 23c toward the upper surface of the flange portion 23b. A spiral groove 23e is formed on the outer peripheral surface of the crankshaft 23 up to the vicinity of the flange portion 23b.

  The eccentric part 23p is formed with a concave center hole 23f from the upper end surface in the axial direction downward. The depth from the upper surface of the center hole 23f is shorter than the axial length of the eccentric portion 23p. Further, the center hole 23f communicates with the upper end portion of the spiral groove 23e through the communication hole 23g.

  A fixed shaft member 23h is inserted into the hollow portion of the main shaft 23a. The fixed shaft member 23h is fixed by a fixture 23i so as not to rotate even when the crankshaft 23 rotates. A fixed shaft spiral groove 23j is formed on the outer peripheral surface of the fixed shaft member 23h. A helical lubricating oil passage is formed by the wall surface of the fixed shaft helical groove 23j and the wall surface of the center hole 23c, and the wall surface is moved by the rotation of the crankshaft 23 (the main shaft 23a), and the lubricating oil becomes viscous due to the viscous effect. So as to rise in the fixed shaft spiral groove 23j.

  The frame 24 has a base 24a that extends in a substantially horizontal direction, and the cylinder 21 is located at the upper part of the base 24a. In addition, a cylindrical radial bearing 26 that extends downward in the vertical direction (toward the bottom surface of the lower case 3n) is formed at a substantially central portion of the frame 24. Further, the frame 24 constitutes a part of the cylinder 21.

  The connecting rod 25 (rod) is a member for connecting the piston 22 and the crankshaft 23, and has a small end portion 25a and a large end portion 25b (end portion on the eccentric portion 23p side). A circular connection hole 25a1 through which the piston pin 29 is inserted is formed in the small end portion 25a so as to penetrate in the vertical direction. A circular connection hole 25b1 through which the eccentric portion 23p is inserted is formed in the large end portion 25b so as to penetrate in the vertical direction.

  The axial direction of the connecting hole 25a1 of the small end portion 25a is configured to be parallel to the axial direction of the piston pin 29. The axial direction of the connecting hole 25b1 of the large end portion 25b is configured to be parallel to the axial direction of the eccentric portion 23p.

  The radial bearing 26 is constituted by a slide bearing on which the main shaft 23a of the crankshaft 23 is supported. Further, the radial bearing 26 has a through hole 26b penetrating in the vertical direction. Further, the radial bearing 26 supports a part of the main shaft 23a. That is, the upper end 26a of the radial bearing 26 is positioned at the substantially lower end of the flange portion 23b, and the lower end 26c of the radial bearing 26 is positioned at the approximate center of the center hole 23c in the height direction.

  The thrust bearing 27 is disposed in a recess 24c formed in a circular groove shape at the opening edge of the through hole 26b of the base 24a. The thrust bearing 27 includes a pair of raceway plates 27a and 27b, a cage 27c, and a rolling element 27d. It arrange | positions between the flange part 23b of the crankshaft 23, and the recessed part 24c.

  The track plate 27a located on the lower side has a ring shape and is disposed so as to be in contact with the bottom surface 24c1 of the recess 24c. The track plate 27b located on the upper side has a ring shape and is disposed so as to contact the lower surface 23b1 of the flange portion 23b.

  The piston pin 29 is inserted through both the connection hole 22a of the piston 22 and the connection hole 25a1 of the small end portion 25a, thereby connecting the piston 22 and the connecting rod 25 in a rotatable manner. Further, the axial direction (the vertical direction in the figure) of the piston pin 29 is configured to be parallel to the axial direction of the connecting hole 22 a of the piston 22.

  Lubricating oil (refrigerating machine oil) that has risen through the intermediate hole 23c is blown out onto the flange portion 23b through the upper communication hole 23d and lubricates the thrust bearing 27. The lubricating oil that has risen in the spiral groove 23e of the crankshaft 23 lubricates between the crankshaft 23 (main shaft 23a) and the radial bearing 26, and passes through the communication hole 23g to pass through the center hole 23f of the eccentric portion 23p. And the area around the connecting rod 25 is lubricated. The lubricating oil that has lubricated the thrust bearing 27 and the like is configured to return to the bottom of the hermetic container 3 through a hole 24s (see FIG. 2) formed in the frame 24.

  The electric element 30 is disposed on the lower side of the frame 24 (below the base 24 a) and includes a rotor 31 and a stator 32.

  The rotor 31 includes a rotor core in which electromagnetic steel plates are laminated, and is fixed to the lower portion of the crankshaft 23 (main shaft 23a) by press-fitting or the like. The rotor 31 has a flat shape in which the radius R is larger than the thickness (the height in the axial direction) T1. Further, the thickness (axial height) T1 of the rotor 31 is set to about half of the length of the radial bearing 26 (bearing length).

  The stator 32 is disposed on the outer periphery of the rotor 31, and is wound with an iron core 32a comprising a cylindrical stator core and a plurality of slots formed on the inner periphery of the stator core, and an iron core 32a via an insulator (not shown). And a rotated coil 32b. Moreover, the iron core 32a has a flat shape in which the length L1 in the radial direction is longer than the thickness (the height in the axial direction) T2 in the longitudinal sectional view of FIG. The coil 32b also has a flat shape in which the length in the radial direction is longer than the thickness (the height in the axial direction) in the longitudinal sectional view of FIG. Further, the thickness (axial height) T2 of the iron core 32a is configured to be approximately the same as the thickness (axial height) T1 of the rotor 31. Thus, when the rotor 31 is flattened, the torque for rotating the rotor 31 can be earned by increasing the diameter of the stator 32 to a flat shape.

  The frame 24 provided with the compression element 20 and the electric element 30 in this way is elastically supported via the plurality of coil springs 9 and 9 in the sealed container 3. Further, the compression element 20 and the electric element 30 are designed with a predetermined clearance CL set in advance so as not to come into contact with the inner wall surface of the sealed container 3 when vibrated during operation.

  The coil spring 9 includes a cylinder 21 side (compressor chamber side Q2, left side of FIG. 1) constituting a part of the compression element 20, and a side opposite to the cylinder 21 side (anti-compressor chamber side Q3, FIG. 1). On the right). In the present embodiment, the coil springs 9 are respectively provided on the front side and the back side in the direction orthogonal to the paper surface of FIG. 1 on each of the compression chamber side and the non-compression chamber side, and a total of four sealed containers 3 are provided. It is configured to be supported by a coil spring 9 (see FIG. 2). All the coil springs 9 have the same shape and spring characteristics. Thus, by making the coil spring 9 a single type, it is possible to prevent an arrangement error in the case where the coil springs 9 are mixed. However, the number of the coil springs 9 is not limited to four, but may be three or five or more.

  In addition, the frame 24 has an extending portion 24 d that extends to the outer peripheral side (radially outer side) than the cylinder 21. The extending portion 24 d extends to the outer peripheral side from the stator 32. In addition, a protrusion 24e that fits and holds the coil spring 9 is formed on the lower surface of the extension 24d.

  Further, the frame 24 has an extending portion 24f extending to the same extent as the extending portion 24d on the side opposite to the extending portion 24d. This extending portion 24 f also extends to the outer peripheral side from the stator 32. A protrusion 24g that fits and holds the upper part of the coil spring 9 is formed on the lower surface of the extension 24f.

  On the bottom surface of the sealed container 3, a stepped portion 3 a is formed on the outer peripheral side of the stator 32 so as to protrude into the sealed container 3. The stepped portion 3a is configured such that a part of the bottom surface and a part of the side surface of the lower case 3n are combined to form a concave shape on the outer surface. Further, the step portion 3 a is provided at a position corresponding to the position of the coil spring 9. In addition, a protrusion 3b is formed on the upper end surface of the step 3a so that the lower portion of the coil spring 9 is fitted and held. The protrusion 3 b is located above the lower surface 31 a of the rotor 31. In addition, the oil surface 40 of the lubricating oil is configured to be positioned below the lower surface 31 a of the rotor 31 so that the lubricating oil is not immersed in the rotor 31. Further, the lower end of the crankshaft 23 (main shaft 23 a) and the lower end of the fixed shaft member 23 h are located below the oil level 40.

FIG. 2 is a cross-sectional view showing the compressor of this embodiment. In addition, in FIG. 2, the flow of the refrigerant | coolant in the compressor 100 is demonstrated.
As shown in FIG. 2, the refrigerant introduced from the suction pipe 3 e that has returned from the refrigerator cooler 66 (see FIG. 6) and connected through the hermetic container 3 passes through the suction port (not shown) of the suction silencer 41. ) And then introduced into the compression chamber Q1 (see FIG. 1) via the head cover 28 and the like. In addition, the refrigerant compressed by the piston 22 in the compression chamber Q1 passes through the discharge chamber space (not shown), passes through the discharge silencers 42a and 42b and the pipe 3f formed in the frame 24, and condenses from the discharge pipe 3g. It is sent to a cooler 66 (see FIG. 4) through a pressure reducer (not shown) and a pressure reducing device (not shown).

  In the compressor 100 configured as described above, the compression element 20 is disposed at the upper part of the frame 24 and the electric element 30 is disposed at the lower part, and the frame 24 is elastically supported in the sealed container 3 via the coil springs 9 and 9. In this case, since the center of gravity is located at the height position of the frame 24 (position comparable to the upper ends of the coil springs 9, 9), the deflection angle of the internal mechanism portion including the compression element 20 and the electric element 30 can be reduced. Further, by arranging the position of the coil spring 9 on the outer peripheral side of the cylinder 21, the vibration of the internal mechanism portion can be further effectively suppressed. Thus, by suppressing the vibration of the internal mechanism portion, the clearance CL (see FIG. 1) between the internal mechanism portion (the compression element 20 and the electric element 30) and the sealed container 3 can be reduced. As a result, the sealed container 3 can be made small, and the compressor 100 can be downsized.

  A rubber seat 10 that elastically supports the hermetic container 3 is provided below each stepped portion 3a (see FIG. 1). The rubber seat 10 is supported by a plate 11 fixed to the lower case 3n of the sealed container 3. The rubber seat 10 is disposed at a position overlapping the coil spring 9 in the vertical direction (up and down direction). By forming the step portion 3a in this manner and arranging the coil spring 9 on the step portion 3a, the coil spring 9 can be installed at a height that does not soak in the lubricating oil. Thus, noise generated when vibrating can be prevented, and the compressor 100 can be quieted. Further, by disposing the rubber seat 10 below the stepped portion 3a, it is possible to prevent the rubber seat 10 from protruding greatly downward from the lower case 3n of the sealed container 3, so that the height of the compressor 100 is increased. Therefore, the compressor 100 can be reduced in size.

Next, means for determining the relationship between the rod pitch P and the spindle length L of the compressor 100 will be described with reference to FIGS. FIG. 3 is an explanatory diagram showing the positional dimensions of each inclination angle by the clearance when obtaining the interference rate in the compressor, FIG. 4 is a graph showing the relationship between the interference rate and COP, and FIG. 5 is the interference rate and spindle length / It is a graph which shows the relationship with a rod pitch. FIG. 3 schematically illustrates the inclination angle due to each clearance for easy understanding.
By the way, an interference factor can be mentioned as one of the factors that determine the COP (Coefficient Of Performance) of the compressor. This interference rate can be obtained by the following equation (1). In the following description of equation (1), the crankshaft is referred to as a shaft, the connecting rod is referred to as a rod, and the cylinder and the radial bearing are referred to as a frame. In the equation (1), α, β, γ, and δ (not shown) are inclination angles due to geometrical tolerances, and A, B, C, D, and E are inclination angles due to clearance. Moreover, about (alpha)-(delta), the diameter dimension of each component actually used is described in the parenthesis writing.
Interference rate = (α + β + γ + δ) / (A + B + C + D + E) (1)
α: Inclination angle due to the parallelism of the shaft (main axis φ18−eccentric portion φ15.9)
β: Inclination angle due to the parallelism of the rod (large end φ15.9−small end φ9.5)
γ: Inclination angle due to the squareness of the piston (outer diameter φ25.4—connection hole φ9.5)
δ: Inclination angle by perpendicularity of frame (cylinder φ25.4-radial bearing φ18)
A: Frame (radial bearing)-Shaft (spindle)
B: Shaft (eccentric part)-Rod (large end)
C: Rod (small end)-Piston pin D: Piston pin-Piston E: Piston-Frame (cylinder)

  α is the parallelism between the main shaft 23a and the eccentric portion 23p of the crankshaft 23. As an example, the diameter (outer diameter) of the main shaft 23a is 18 mm, and the diameter (outer diameter) of the eccentric portion 23p is 15.9 mm. Is. β is the parallelism between the small end portion 25a and the large end portion 25b of the connecting rod 25. As an example, the diameter of the connecting hole 25b1 of the large end portion 25b is 15.9 mm, and the connecting hole 25a1 of the small end portion 25a is The diameter of this is 9.5 mm. γ is a perpendicular angle between the outer diameter of the cylindrical portion of the piston 22 and the connecting hole 22a into which the piston pin 29 is inserted. As an example, the outer diameter is 25.4 mm, and the diameter (outer diameter) of the connecting hole 22a is It is 9.5 mm. δ is a perpendicular angle between the axial direction of the cylinder 21 in the frame 24 (the horizontal direction in the figure) and the axial direction of the radial bearing 26 (the vertical direction in the figure). As an example, the inner diameter of the cylinder 21 is 25.4 mm. The diameter (inner diameter) of 26 is 18 mm.

  As shown in FIG. 3, A is an inclination angle when the main shaft 23 a is inclined in the radial bearing 26 due to the clearance between the main shaft 23 a of the crankshaft 23 and the radial bearing 26. B is an inclination angle when the eccentric portion 23p is inclined in the large end portion 25b by the clearance between the large end portion 25b of the connecting rod 25 and the eccentric portion 23p of the crankshaft 23. C is an inclination angle when the piston pin 29 is inclined in the small end portion 25a due to the clearance between the small end portion 25a of the connecting rod 25 and the piston pin 29. D is an inclination angle when the piston pin 29 is inclined in the connection hole 22a due to the clearance between the piston pin 29 and the connection hole 22a of the piston 22. E is an inclination angle when the piston 22 is inclined in the cylinder 21 due to the clearance between the piston 22 and the cylinder 21 of the frame 24.

Then, when tanA, tanB, tanC, tanD, and tanE are obtained from the inclination angles A, B, C, D, and E shown in FIG. 3, they can be expressed by the following equations (2) to (6). Note that “× 1000” described in the equations (2) to (6) is for adjusting the unit system to millimeters because the unit of clearance is micrometer.
tanA = CLa / (La × 1000) (2)
tanB = CLb / (Lb × 1000) (3)
tanC = CLc / (Lc × 1000) (4)
tanD = CLd / (Ld × 1000) (5)
tanE = CLe / (Le × 1000) (6)
Note that CLa is a distance that the main shaft 23a and the radial bearing 26 are separated from each other at the end (lower end) in the axial direction of the radial bearing 26, and La is a sliding length of the radial bearing 26 on which the main shaft 23a slides. . CLb is a distance that the eccentric part 23p and the large end part 25b are separated from each other at the end (upper end) in the axial direction of the large end part 25b, and Lb is a sliding distance of the large end part 25b on which the eccentric part 23p slides. It is long. CLc is a distance at which the piston pin 29 and the small end 25a are separated from each other at the end (lower end) in the axial direction of the small end 25a, and Lc is a sliding distance of the small end 25a on which the piston pin 29 slides. It is long. CLd is a distance that the connecting hole 22a of the piston 22 and the piston pin 29 are separated from each other at an end (upper end) in a direction orthogonal to the axial direction of the piston 22, and Ld is a connecting hole 22a in which the piston pin 29 slides. Is the sliding length. CLe is a distance at which the cylinder 21 and the piston 22 are separated from each other at the end of the piston 22 in the axial direction, and Le is a sliding length of the cylinder 21 on which the piston 22 slides.

When A to E are obtained from the above equations (2) to (6), the following equations (7) to (11) are obtained.
A = arctan (CLa / (La × 1000) (7)
B = arctan (CLb / (Lb × 1000) (8)
C = arctan (CLc / (Lc × 1000) (9)
D = arctan (CLd / (Ld × 1000) (10)
E = arctan (CLe / (Le × 1000) (11)
Thus, when each inclination-angle AE is represented collectively, it will become a formula (12) shown below.
arctan (each clearance / (sliding length × 1000)) (12)

  By the way, when the relationship between the interference rate obtained from the above-described equation (1) and the COP was examined, it was confirmed that a relationship in which the COP increases as the interference rate decreases as shown in FIG. It was. Therefore, it has been confirmed that the COP of the compressor 100 can be increased by obtaining the interference rate from the relationship shown in FIG.

  Accordingly, the spindle length L when the length of the spindle length L (see FIG. 1) is changed with a numerical value other than the inclination angle A of the expression (1) related to the length of the crankshaft 23 as a fixed value. FIG. 5 shows a plurality of plotted relations between the ratio (L / P) of the rod pitch P (see FIG. 1) and the interference rate. As shown in FIG. 1, the main shaft length L in the present embodiment means the length from the upper end of the main shaft 23a of the crankshaft 23, in other words, from the lower surface 23b1 of the flange portion 23b to the lower end of the radial bearing 26. . As shown in FIG. 1, the rod pitch P means a distance connecting the rotation center (axis center) c1 of the small end portion 25a of the connecting rod 25 and the rotation center (axis center) c2 of the large end portion 25b. Therefore, by shortening the main shaft length L, L / P (main shaft length / rod pitch) decreases, and by increasing the main shaft length L, L / P increases.

  As shown in FIG. 5, it was confirmed that the interference rate increased as L / P increased. In addition, it was confirmed that an inflection point exists when L / P is near 1.1. That is, when L / P is 1.1 or less, the interference rate changes along the straight line S1, and when L / P exceeds 1.1, the interference rate changes along the straight line S2. Was confirmed. Thus, when L / P is 1.1 or less, the spindle length L can be shortened while lowering the interference rate. When L / P exceeds 1.1, the interference rate increases and the spindle length L increases. Thus, by setting L / P to 1.1 or less, the crankshaft 23 can be shortened to reduce the size of the compressor 100, and the performance of the compressor 100 can be ensured to prevent malfunction. (The crankshaft 23 can be prevented from locking). Further, until now, shortening the spindle length L (reducing the size of the compressor 100) has increased the bearing load, and has not been actively adopted so far. However, even if the spindle length L is shortened, by setting L / P to 1.1 or less, an increase in bearing load accompanying the shortening of the spindle length can be allowed, and the performance as the compressor 100 is ensured. However, it was confirmed that downsizing becomes possible.

  Further, in order to improve the performance of the compressor 100, when the connection method of the piston 22 and the connecting rod 25 is changed from a ball joint to a piston pin method, high dimensional accuracy is required. However, since the inclination angle of the crankshaft 23 is increased by shortening the main shaft length L, the accuracy of geometric tolerance can be relaxed. Further, by shortening the main shaft length L, the space in which the center hole 23c into which the fixed shaft member 23h of the crankshaft 23 is inserted is narrowed. By narrowing this space, the region of the thin cylindrical portion is also narrower than when the crankshaft is long, so that the rigidity of the crankshaft 23 can be increased accordingly. By suppressing the bending deformation of the crankshaft 23, the performance as the compressor 100 can be ensured even if the crankshaft 23 is shortened and the compressor 100 is downsized.

  In the present embodiment, in the compressor 100, when the height of the small end portion 25a in the axial direction is H (see FIG. 1), the main shaft length L is set to 3 to 5 times the height H. The accuracy of the parallelism between the axial direction of the piston pin 29 and the axial direction of the main shaft 23a (center axis O) can be relaxed. Therefore, even if the crankshaft 23 is shortened to reduce the size of the compressor 100, the performance as the compressor 100 can be ensured.

  FIG. 6: shows the schematic sectional drawing of the refrigerator carrying the compressor of this embodiment, (a) is the structure which has arrange | positioned the compressor in the lower part, (b) is the structure which has arrange | positioned the compressor in the upper part.

  As shown in FIG. 6A, the refrigerator 60A is configured by dividing the refrigerator main body 61 into a plurality of storage chambers 62, 63, 64, 65. For example, the storage room 62 is a refrigerated room, the storage room 63 is an upper freezer room, the storage room 64 is a lower freezer room, and the storage room 65 is a vegetable room. The positional relationship between the storage chambers 62, 63, 64, 65 is not limited to that shown in FIG. The compressor 100 is disposed in a machine room at a lower part on the back side of the drawer 65 a of the storage room 65 (the lowermost end on the back side of the refrigerator main body 61). The refrigerant discharged from the compressor 100 passes through a condenser (not shown) and a decompression mechanism (not shown) provided in the refrigerator 60A, absorbs heat in the refrigerator by the cooler 66, and is again compressed. Returned in.

  By the way, when a tall compressor is applied as in the prior art, it is necessary to increase the volume of the machine room, so that the capacity of the drawer 65a stored in the storage chamber 65 becomes small (shallow drawer). Therefore, by adopting the refrigerator 60A to which the compressor 100 of the present embodiment is applied, the volume of the machine room can be reduced and the height position of the ceiling surface of the machine room can be lowered. It becomes possible to expand the storage capacity on the side.

  As shown in FIG. 6B, in the refrigerator 60B, the compressor 100 is disposed in the machine room at the upper back side of the storage room 62 (the uppermost rear side of the refrigerator main body 61).

  By the way, when a tall compressor is applied as in the prior art, the vibration generated by the compressor is large, so the vibration transmitted to the refrigerator body is also large. Therefore, by adopting the refrigerator 60B to which the compressor 100 of the present embodiment is applied, the vibration can be reduced by the above-described structure, so that the vibration transmitted to the refrigerator main body 61 can be suppressed. Further, by applying the small compressor 100, it is possible to increase the internal capacity of the storage chamber 62.

  The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention. For example, in this embodiment, the case where the piston 22 and the connecting rod 25 are connected by the piston pin 29 has been described as an example. However, the present invention is not limited to the piston pin 29, and a ball joint method may be adopted. Good.

3 Sealed container (container)
DESCRIPTION OF SYMBOLS 9 Coil spring 10 Rubber seat 20 Compression element 21 Cylinder 22 Piston 23 Crankshaft 23a Main shaft 23b Flange part 23p Eccentric part 24 Frame 24a Base 24b Through-hole 24c Recessed part 24d Extension part 25 Connecting rod (rod)
25a Small end portion 25a1 Connection hole 25b Large end portion 25b1 Connection hole 26 Radial bearing (bearing)
27 Thrust bearing 28 Head cover 29 Piston pin 30 Electric element 31 Rotor 32 Stator 100 Compressor A to E Inclination angle H Small end height L Spindle length P Rod pitch Q2 Compressor chamber side Q3 Anti-compressor chamber side

Claims (3)

In a compressor comprising: a compression element; an electric element that drives the compression element; and a container that houses the compression element and the electric element.
The compression element includes a cylinder, a piston that compresses the refrigerant by reciprocating in the cylinder, a crankshaft that rotates eccentrically by the electric element, and an eccentric portion of the crankshaft and the piston that are rotatably connected to each other. And a bearing that supports the crankshaft,
When the length in the axial direction from the upper end of the main shaft of the crankshaft to the lower end of the bearing is L, and the distance connecting the rotation center at one end of the rod and the rotation center at the other end is P, L / P The compressor characterized by being 1.1 or less. A piston pin that rotatably connects the piston and the rod;
2. The compressor according to claim 1, wherein L / H is 3 to 5 where H is an axial height of an end portion of the piston pin.   A refrigerator comprising the compressor according to claim 1 or 2.

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