Compressor

Abstract

The present invention provides a compressor with improved reliability of a leaf spring. The compressor of the present invention includes: an electric motor; a drive shaft having an eccentric portion; a compression mechanism portion that compresses refrigerant; and a hermetic container. The compression mechanism portion includes: an annular cylinder block; an annular roller that has an eccentric portion disposed therein and revolves within the cylinder block; a first bearing that is provided on one axial side of the cylinder block and axially supports the drive shaft; a second bearing that is provided on the other axial side of the cylinder block and axially supports the drive shaft; a vane whose tip contacts the outer peripheral surface of the roller; and a leaf spring that presses the vane toward the outer peripheral surface of the roller. When the outer diameter of the vane side of the effective winding portion is set as D1, the diameter at the change point between the effective winding portion and the closely wound portion is set as D2, and the diameter of the vane side of the closely wound portion is set as D3, the leaf spring has a relationship of D1 < D2 < D3, and each of the portions between D1 and D2 and between D2 and D3 is constituted by one tapered portion.

Description

Technical Field

[0001] The present invention relates to a compressor. Background Art

[0002] In air conditioners and the like, a rotary compressor is used as the compressor.

[0003] In a rotary compressor, even when starting under the condition that the pressure difference between the inside and outside of the compression chamber in the machine is small, the vane is brought into contact with the roller to form a compression chamber. Therefore, a vane spring for pressing the vane against the roller is provided.

[0004] The vane spring has a function of pressing the vane against the pressing roller from the back surface by using a spring load. Therefore, the spring itself needs to have a fixing force capable of fixing itself with respect to the spring load. As a structure for ensuring the fixing force, a structure in which the closely wound portion of the vane spring is pressed into the pump is mostly adopted.

[0005] In the design of the vane spring, with the flattening of the pump of the rotary compressor and the enlargement of the compression chamber in recent years, the installation space has become smaller. However, the vane spring needs to ensure the spring load, the number of repeated fatigue cycles, the fixing force, and the safety of expansion and contraction. Therefore, it has become a problem to balance each design point.

[0006] In Patent Document 1, a diameter difference is provided between the effective wound portion Da and the closely wound portion Db. Moreover, by making a part of the effective wound portion Da and the closely wound portion Db into a tapered portion, contact between the outer diameter of the spring during spring expansion and contraction and the hole for spring installation is avoided.

[0007] In Patent Document 2, only a part of the effective wound portion and the closely wound portion is formed into a tapered portion, and the closely wound portion (end ground wound portion) that becomes the press-fitting portion into the pump component is formed into multiple turns of the same diameter, thereby ensuring the fixing force of the spring itself with respect to the spring load.

[0008] Prior Art Documents

[0009] Patent Document 1: Japanese Patent No. 3927331 ([[]] Figure 2 etc.)

[0010] Patent Document 2: Japanese Patent No. 5810221 (FIG. 9B etc.)

[0011] In Patent Document 1, since there is a difference in diameter between the effective winding portion Da and the closely wound portion Db, it is possible to avoid contact between the outer diameter surface of the spring during spring expansion and contraction and the hole for spring installation. However, only through the tapered portion of a part of the effective winding portion, the outer diameter difference between adjacent coils at the portion where the coil outer diameter changes from the effective winding portion Da to the closely wound portion Db becomes large. When the spring expansion and contraction amplitude becomes large due to liquid compression or the like, the adjacent coils of the tapered portion enter inwardly, and there is a possibility of breakage due to the friction of the spring itself. In addition, since the closely wound portion Db, which is the fixing portion of the spring itself, is wound only once, the fixing force of the spring with respect to the spring load may be insufficient.

[0012] In Patent Document 2, since the closely wound portion (end-flattened winding portion) has multiple turns of the same diameter, it is easy to ensure the fixing force of the spring with respect to the spring load. However, in a pump where the overall length of the closely wound portion is likely to be long and the spring installation space is small, as in Patent Document 1, the outer diameter difference between adjacent coils at the portion where the coil outer diameter changes from the effective winding portion to the closely wound portion is likely to become even larger. Therefore, when the spring expansion and contraction amplitude becomes large due to liquid compression or the like, there is a possibility that the adjacent coils of the coil tapered portion enter inwardly, and the possibility of breakage caused by the friction of the spring itself increases. Summary of the Invention

[0013] The present invention has been completed in view of the above actual situation, and an object thereof is to provide a compressor with improved reliability of a leaf spring.

[0014] To solve the above problems, the compressor of the present invention includes: a motor having a stator and a rotor; a drive shaft that rotates integrally with the rotor and has an eccentric portion; a compression mechanism portion that compresses refrigerant as the drive shaft rotates; and a hermetic container that houses the motor, the drive shaft, the compression mechanism portion, and lubricating oil. The compression mechanism portion includes: an annular cylinder block; an annular roller that has the eccentric portion disposed therein and revolves in the cylinder block as the motor is driven; a first bearing that is provided on one axial side of the cylinder block and axially supports the drive shaft; a second bearing that is provided on the other axial side of the cylinder block and axially supports the drive shaft; a blade whose tip contacts the outer peripheral surface of the roller and divides the cylinder chamber formed between the cylinder block and the roller into a suction chamber and a compression chamber; and a leaf spring that presses the blade toward the outer peripheral surface of the roller. When the outer diameter of the blade side of the effective winding portion is set as D1, the diameter of the change point between the effective winding portion and the closely wound portion is set as D2, and the diameter of the blade side of the closely wound portion is set as D3, the leaf spring has a relationship of D1 < D2 < D3. The tapered portion between D1 and D2 and the tapered portion between D2 and D3 are each constituted by one tapered portion, and the tapered portion between D2 and D3 is larger than the tapered portion between D1 and D2.

[0015] The effects of the present invention are as follows.

[0016] According to the present invention, a compressor with improved reliability of a leaf spring can be provided. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 is a longitudinal sectional view of a compressor according to an embodiment of the present invention.

[0018] Figure 2 is Figure 1 the sectional view taken along the line I-I of

[0019] Figure 3 is an enlarged side view of the periphery of the leaf spring.

[0020] Figure 4 is a sectional view taken along the side when the leaf spring of the modified example is compressed.

[0021] In the figures: 1 - sealed container, 2 - motor, 2a - stator, 2b - rotor, 4 - crankshaft (drive shaft), 4b - eccentric portion, 5 - compression mechanism portion, 5c - upper bearing (first bearing), 5d - lower bearing (second bearing), 5a - cylinder block, 5b - roller, 5e - vane, 7, 17 - leaf springs, 7a, 17a - effective winding portions, 7b, 17b - closely adhering winding portions, 7d, 17d - fixing portions of the closely adhering winding portions, C - compressor, Cm - compression chamber, Cy - cylinder block chamber, d - coil wire diameter, D1 - outer diameter on the vane side, D2 - diameter at the change point between the effective winding portion and the closely adhering winding portion, D3 - outer diameter on the vane side of the closely adhering winding portion, Da, Db - outer diameters of adjacent coils, In - suction chamber, t1 - tapered portion between D1 and D2, t2 - tapered portion between D2 and D3, t21 - tapered portion between D1 and D2 at full compression, t22 - tapered portion between D2 and D3 at full compression, θ1 - angle of the tapered portion of the effective winding portion at full compression, θ2 - angle of the tapered portion of the closely adhering winding portion at full compression. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0022] The present invention relates to a technique in which a part of the effective winding portion and the closely adhering winding portion of a leaf spring in a compressor is configured in a conical shape.

[0023] Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings as appropriate.

[0024] Figure 1 shows a longitudinal sectional view of a compressor C according to an embodiment of the present invention.

[0025] The compressor C is connected to a gas-liquid separator (not shown) via an intake pipe Pi. The gas-liquid separator separates the refrigerant liquid mixed in the refrigerant vapor and allows only the gaseous refrigerant to be sucked into the compressor C through the intake pipe Pi. This is because liquid compression can cause damage to the compressor C.

[0026] <Structure of Compressor C>

[0027] The compressor C is a rotary compressor that compresses gaseous refrigerant. The compressor C includes a sealed container 1, an electric motor 2, a crankshaft 4, a compression mechanism section 5, and a silencer cover 6.

[0028] The sealed container 1 is a shell-shaped container that houses the electric motor 2, the crankshaft 4, the compression mechanism section 5, etc. The sealed container 1 is sealed to house the compressed high-pressure refrigerant.

[0029] The sealed container 1 has a cylindrical barrel chamber 1a, a cover chamber 1b at the upper end, and a bottom chamber 1c at the lower end. The cover chamber 1b is welded to the upper end of the barrel chamber 1a. The bottom chamber 1c is welded to the lower end of the barrel chamber 1a.

[0030] The crankshaft 4 is driven by the electric motor 2.

[0031] The compression mechanism section 5 compresses the gaseous refrigerant by the rotational movement of the crankshaft 4.

[0032] An oil storage section U for storing lubricating oil is provided at the bottom of the sealed container 1.

[0033] Figure 2 Indicates Figure 1 the I-I cross-sectional view.

[0034] In order to improve the lubricity of the compressor C and the sealing performance of the compression chamber Cm (refer to Figure 2 ), lubricating oil is sealed.

[0035] As Figure 1 shown, the intake pipe Pi is inserted and fixed in the barrel chamber 1a of the sealed container 1.

[0036] The intake pipe Pi is a pipe that guides the gaseous refrigerant to the cylinder chamber Cy of the compression mechanism section 5 (refer to Figure 2 ).

[0037] In Figure 1 the shown cover chamber 1b of the sealed container 1, the discharge pipe Po is inserted and fixed. The discharge pipe Po is a pipe that guides the refrigerant compressed by the compression mechanism section 5 to the outside of the compressor C.

[0038] An electric motor 2 is provided inside the sealed container 1. The electric motor 2 includes a stator 2a, a rotor 2b, and a winding 2c.

[0039] The stator 2a is a cylindrical component fixed to the inner peripheral wall of the cylindrical chamber 1a. The stator 2a is laminated with electromagnetic steel sheets, and a predetermined number of windings 2c are wound around the poles formed by the electromagnetic steel sheets. A current flows through the windings 2c to form a magnetic field on the poles of the electromagnetic steel sheets.

[0040] The rotor 2b is a cylindrical component formed by laminating electromagnetic steel sheets and is disposed radially inside the stator 2a. A crankshaft 4 is fixed to the rotor 2b by press-fitting or the like. In addition, a permanent magnet can also be used for the rotor 2b.

[0041] Figure 1 The illustrated crankshaft 4 extends in the vertical direction and rotates integrally with the rotor 2b by the drive of the motor 2. The rotor 2b of the motor 2 is coaxially fixed to the main shaft 4a.

[0042] The crankshaft 4 is rotatably supported by an upper bearing 5c and a lower bearing 5d. The crankshaft 4 includes a main shaft 4a and an eccentric portion 4b. The eccentric portion 4b is integrally formed with the main shaft 4a.

[0043] The eccentric portion 4b forms a shaft that rotates while being eccentric with respect to the main shaft 4a.

[0044] The eccentric portion 4b is disposed inside a circular roller 5b provided radially inside a ring-shaped cylinder block 5a at the lower part of the crankshaft 4. The eccentric portion 4b causes the roller 5b to revolve around the center O of the crankshaft 4 by rotation.

[0045] A predetermined oil supply passage 4c is provided axially at the lower center inside the crankshaft 4. The oil supply passage 4c is a flow path that guides the lubricating oil in the oil storage portion U of the closed container 1 to the compression mechanism portion 5 and the like.

[0046] Lubricating oil is supplied to the radial inside of the roller 5b via a longitudinally elongated transverse hole h3 provided in the eccentric portion 4b. In this way, the space inside the radial side of the roller 5b communicates with the oil supply passage 4c of the crankshaft 4. The oil supply passage 4c opens into the oil storage portion U at the lower end of the crankshaft 4.

[0047] Near the lower end of the crankshaft 4 corresponding to the upstream of the oil supply passage 4c, a thin plate-shaped metal piece (not shown) that is torsionally bent as predetermined and functions as an oil pump is provided. As the thin plate-shaped metal piece rotates integrally with the crankshaft 4, the lubricating oil is sucked into the oil supply passage 4c.

[0048] A plurality of transverse holes h1, h2, and h3 communicating with the oil supply passage 4c are provided in the crankshaft 4. The sliding surface of the upper bearing 5c is lubricated by the lubricating oil supplied from the transverse hole h1. The sliding surface of the lower bearing 5d is lubricated by the lubricating oil supplied from the transverse hole h2.

[0049] Further, lubricating oil is supplied radially inward of the roller 5b through the longitudinally elongated transverse hole h3 provided in the eccentric portion 4b. In this way, the space radially inward of the roller 5b communicates with the oil supply passage 4c of the crankshaft 4.

[0050] Figure 1 The compression mechanism portion 5 shown compresses the refrigerant as the crankshaft 4 rotates. The compression mechanism portion 5 is disposed below the electric motor 2.

[0051] <Compression mechanism portion 5>

[0052] The compression mechanism portion 5 compresses the refrigerant sucked through the suction pipe Pi in the compression chamber Cm and discharges the compressed refrigerant into the cylinder chamber 1a.

[0053] The compression mechanism portion 5 includes a cylinder block 5a, a roller 5b, an upper bearing 5c, a lower bearing 5d, a vane 5e, a discharge valve 5f, and a vane spring 7.

[0054] As Figure 2 shown, the cylinder block 5a, together with the roller 5b, the upper bearing 5c (refer to Figure 1 ), and the lower bearing 5d, forms a cylinder chamber Cy. The cylinder chamber Cy refers to the space formed between the cylinder block 5a and the roller 5b.

[0055] The vane 5e is pressed by the vane spring 7, and the front end on the roller 5b side contacts the outer peripheral surface of the roller 5b. Figure 2 The vane 5e shown divides the cylinder chamber Cy between the cylinder block 5a and the roller 5b into a suction chamber (not shown) and a compression chamber Cm. The gaseous refrigerant is supplied to the suction chamber through the suction pipe Pi.

[0056] The cylinder chamber Cy is a space formed by the suction chamber or / and the compression chamber Cm. That is, the cylinder chamber Cy includes the compression chamber Cm and the suction chamber.

[0057] In Figure 2 , the front end of the vane 5e retreats to the inner peripheral surface of the cylinder block 5a through the roller 5b, and the entire cylinder chamber Cy becomes the compression chamber Cm. That is, Figure 2 indicates the end of the suction of the refrigerant into the suction chamber and the start time of compressing the sucked refrigerant.

[0058] The roller 5b is disposed in the cylinder chamber Cy, and the eccentric portion 4b (refer to Figure 1 , Figure 2 ) is disposed on the inner periphery. The roller 5b is pressed by the vane 5e, so that the inner peripheral surface of the roller 5b slidably contacts the outer peripheral surface of the eccentric portion 4b. The roller 5b is pressed by the vane 5e and the eccentric portion 4b as the electric motor 2 (refer to Figure 1 ) is driven, and revolves around the center O of the crankshaft in the cylinder block 5a.

[0059] The eccentric portion 4b constitutes a crankshaft 4 that transmits the rotation of the motor 2 to the roller 5b. The rotation axis of the eccentric portion 4b coincides with the rotation axis (center O of the crankshaft) around which the roller 5b revolves. When the eccentric portion 4b rotates by the motor 2, the roller 5b is pressed against the vane 5e, and the outer peripheral surface of the eccentric portion 4b and the inner peripheral surface of the roller 5b slide by forming a sliding bearing, and the rotation of the eccentric portion 4b is transmitted to the roller 5b.

[0060] Figure 3 Indicates Figure 1 An enlarged side view of the periphery of the leaf spring 7 shown.

[0061] A spring hole 5e1 for arranging the vane 5e is formed in the vane 5e.

[0062] The leaf spring 7 is a compression coil spring. The leaf spring 7 has an effective winding portion 7a and a tight winding portion 7b. The effective winding portion 7a expands and contracts to function as a spring. The fixing portion 7d of the tight winding portion 7b is the fixing portion of the leaf spring 7. The tight winding portion 7b is fixed to the fixing portion 1a1 of the cylinder chamber 1a by press-fitting.

[0063] The leaf spring 7 is arranged such that the effective winding portion 7a does not contact the spring hole 5e1 of the vane 5e. That is, it is configured such that the effective winding portion 7a does not contact the spring hole 5e1 of the vane 5e when the leaf spring 7 expands and contracts. This is because when the leaf spring 7 contacts (friction) the spring hole 5e1 of the vane 5e, the leaf spring 7 is damaged.

[0064] Let the outer diameter on the vane 5e side of the effective winding portion 7a be D1, the diameter at the change point between the effective winding portion 7a and the tight winding portion 7b be D2, and the diameter on the vane 5e side of the fixing portion 7d of the tight winding portion 7b be D3.

[0065] Among D1, D2, and D3, the following relationship holds:

[0066] D1 < D2 < D3 (1).

[0067] Moreover, the leaf spring 7 Figure 3 In the side view shown, a tapered portion t1, t2 having one taper (inclination) is formed between D1 and D2 and between D2 and D3, respectively.

[0068] Therefore, it is possible to reduce the maximum value of the outer diameter difference between adjacent coils 7c at the portion (point) where the coil outer diameter changes from the effective winding portion 7a to the tight winding portion 7b.

[0069] Thus, even when the spring expansion and contraction length becomes large due to liquid compression of the refrigerant or the like, by using the tapered portions t1, t2, it is possible to effectively suppress adjacent coils 7c from entering each other toward the inside of the coil 7c. Therefore, the reliability of the leaf spring 7 is improved.

[0070] In addition, as shown in the following formula (2), the difference between the outer diameters Da and Db of adjacent coils 7c in the leaf spring 7 is equal to or less than the coil wire diameter d:

[0071] Db - Da ≤ d (2).

[0072] Since the difference in the outer diameters Db - Da of adjacent coils 7c is equal to or less than the coil wire diameter d, even when the spring expansion / contraction length increases due to liquid compression of the refrigerant or the like, it is possible to mechanically suppress the inward entry of adjacent coils 7c into each other by the tapered portions t1 and t2. Therefore, the normal expansion / contraction operation of the leaf spring 7 is maintained, and the reliability of the leaf spring 7 is improved.

[0073] In addition, the fixing portion 7d having the diameter D3 in close contact with the winding portion 7b has multiple turns.

[0074] By setting the tapered portions t1 and t2 to one taper (incline) each, it is possible to reduce the maximum value of the difference in the outer diameters Db - Da of adjacent coils 7c in a small space. Thereby, it is possible to miniaturize the effective winding portion 7a and increase the space of the winding portion 7b in close contact. Therefore, the fixing portion 7d having the diameter D3 in close contact with the winding portion 7b can be made to have multiple turns. As a result, the fixing force of the leaf spring 7 with respect to the spring load increases.

[0075] (Advantages of the Invention)

[0076] Even when the spring expansion / contraction length increases due to liquid compression or the like, it is possible to effectively suppress the inward entry of adjacent coils 7c into each other by the tapered portions t1 and t2. Since it is possible to reduce the difference in the outer diameters Db - Da of adjacent coils 7c, it is possible to miniaturize the effective winding portion 7a. Therefore, the winding portion 7b in close contact can be made to have multiple turns, and the fixing of the winding portion 7b in close contact can be performed reliably.

[0077] Therefore, the reliability of the leaf spring 7 is improved.

[0078] <Variation>

[0079] Figure 4 A cross-sectional view showing the side view of the leaf spring 17 representing the variation when compressed.

[0080] The outer diameter on the blade 5e side of the effective winding portion 17a is set to D11, the diameter at the change point between the effective winding portion 17a and the winding portion 17b in close contact is set to D12, and the diameter on the blade 5e side of the fixing portion 17d of the winding portion 17b in close contact is set to D13.

[0081] When the leaf spring 17 in the modified example extends, a tapered portion (inclination) is formed between the outer diameter D11 and the diameter D12, and a tapered portion (inclination) is formed between the diameter D12 and the diameter D13.

[0082] And, as Figure 4 shown, in a side view, when the leaf spring 17 is fully compressed, the taper angle θ1 of the tapered portion t21 of the effective winding portion 17a is substantially the same as (the same or substantially the same as) the taper angle θ2 of the tapered portion t22 of the adjacent winding portion 17b.

[0083] The taper angle θ1 of the tapered portion t21 ≈ the taper angle θ2 of the tapered portion t22 (3).

[0084] According to the modified example, the angles (θ1, θ2) of the tapered portions t21 and t22 of the effective winding portion 17a and the adjacent winding portion 17b when the leaf spring 17 is fully compressed are substantially the same. Therefore, in the adjacent winding portion 17b except for the effective winding portion 17a and the fixing portion 17d, the maximum value of the outer diameter difference of the adjacent coils 17c can be reduced.

[0085] Therefore, even when the spring expansion and contraction length of the leaf spring 17 becomes larger due to liquid compression or the like, the adjacent coils 17c can be effectively suppressed from entering each other inward by the tapered portions t21 and t22. Therefore, the reliability of the leaf spring 17 is improved.

[0086] <<Other Embodiments>>

[0087] 1. In the above-described embodiments and modified examples, the compressor C having a single compression chamber Cm is taken as an example for explanation, but the present invention can of course be applied to a compressor having a plurality of compression chambers vertically divided by a partition plate.

[0088] 2. The present invention is not limited to the structures of the above-described embodiments and modified examples, and various deformation modes and specific modes can be carried out within the scope of the appended technical solutions.

Claims

1. A compressor, characterized in that, it comprises: a motor having a stator and a rotor; a drive shaft that rotates integrally with the rotor and has an eccentric portion; a compression mechanism portion that compresses a refrigerant as the drive shaft rotates; and a hermetic container that houses the motor, the drive shaft, the compression mechanism portion, and lubricating oil, the compression mechanism portion having: a ring-shaped cylinder block; a ring-shaped roller that has the eccentric portion disposed therein and revolves within the cylinder block as the motor is driven; a first bearing provided on one axial side of the cylinder block and axially supporting the drive shaft; a second bearing provided on the other axial side of the cylinder block and axially supporting the drive shaft; a vane whose tip contacts the outer peripheral surface of the roller and divides a cylinder chamber formed between the cylinder block and the roller into a suction chamber and a compression chamber; and a vane spring that presses the vane toward the outer peripheral surface of the roller, when the outer diameter on the vane side of the effective winding portion is set as D1, the diameter at the change point between the effective winding portion and the tightly wound portion is set as D2, and the diameter on the vane side of the tightly wound portion is set as D3, the vane spring has a relationship of D1 < D2 < D3, when viewed from the side, the portion between D1 and D2 and the portion between D2 and D3 are each constituted by a conical portion, the conical portion between D2 and D3 is larger than the conical portion between D1 and D2, when viewed from the side, the angle of the conical portion of the effective winding portion when the vane spring is fully compressed is substantially the same as the angle of the conical portion of the tightly wound portion.

2. The compressor according to claim 1, characterized in that, the difference in outer diameter between adjacent coils is equal to or less than the wire diameter of the coil wire.

3. The compressor according to claim 1, characterized in that, the fixed portion of the tightly wound portion is multiple turns.

4. The compressor according to claim 2, characterized in that, the fixed portion of the tightly wound portion is multiple turns.

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