JPH1037868A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure a sufficient injection flow and the efficiency of a compressor, and sufficiently improve heating ability. SOLUTION: An injection port 51 is arranged in a position where injection is started before a compression chamber 13 sucks a refrigerant and is closed, the diameter D of the injection port 51 is set to be approximately the same as the dimension of the width B of a chip seal 61 between a slewing scroll 12 and a fixed scroll 11 arranged on the end surface of the lap 12a of the slewing scroll 12, and the lap thickness T12 of the slewing scroll 12 is formed thicker than that of the fixed scroll 11.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor mainly used for refrigeration and air conditioning for business use and home use.

[0002]

2. Description of the Related Art Electric compressors for refrigeration and air conditioning include those having a reciprocating compressor and a rotary compressor. Currently, it is growing by making use of its features in terms of cost and performance. Among them, scroll type compressors have been put to practical use taking advantage of the features of high efficiency, low noise, and low vibration.

[0003] JP-A-63-243481, 2 discloses a
Disclosed is a scroll compressor that performs gas injection into a compression chamber between a fixed scroll and an orbiting scroll through an injection port to improve heating capacity.

[0004] By such gas injection, the capacity of heating by the refrigerating cycle using the scroll compressor can be improved by the amount of supercharging of the refrigerant.

[0005] In particular, the one disclosed in the above-mentioned publication performs injection after the compression chamber is closed. By making the diameter of the injection port larger than the thickness of the wrap of the orbiting scroll, the supercharging amount of the gas refrigerant is increased. To further improve the heating capacity.

[0006]

When the injection is performed in a state where the compression chamber is closed as in the above-described prior art, the pressure required for the injection increases by the amount of the pressure in the compression chamber, and the injection flow rate of the refrigerant increases. Is small, it is difficult to obtain a sufficient supercharged state. Therefore, even if the diameter of the injection port is larger than the thickness of the wrap as disclosed in the above publication, the injection flow rate is small due to the effect of the pressure in the compression chamber if the injection into the closed compression chamber is performed, and the heating capacity is sufficient. Can not be improved. In addition, the injection port having a diameter larger than the thickness of the wrap of the orbiting scroll is partitioned by the wrap while the wrap is positioned over the wrap.
Since the gas refrigerant communicates with both of the two compression chambers, the gas refrigerant in the high-pressure side compression chamber that discharges the gas refrigerant first out of the two compression chambers leaks into the low-pressure side compression chamber that discharges the gas refrigerant later. Therefore, the amount of recirculation in the compression chamber increases and the efficiency of the scroll compressor decreases.

When the room temperature approaches the set temperature during cooling and heating, the normal operation of about 60 to 90 Hz
In particular, in the case of performing an energy saving operation in which the annual consumption is reduced by switching to a low speed operation of about Hz, the leakage of the gas refrigerant increases, and the efficiency of the scroll compressor is greatly reduced.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned conventional problems and to provide a scroll compressor capable of guaranteeing a sufficient injection flow rate and efficiency and sufficiently improving a heating capacity. It is assumed that.

[0009]

In order to achieve the above object, a first aspect of the present invention is to provide a scroll scroll in which gas injection is performed through a fuel injection port between a fixed scroll and an orbiting scroll through an injection port. In the compressor, an injection port is provided at a position where injection is started before the compression chamber sucks the refrigerant and is closed.

In such a configuration, the injection is started before the compression chamber sucks the refrigerant and closed, and the injection timing is selected immediately after the start of the injection so that the injected gas refrigerant can be cooled. There is no backflow to the suction side, and the pressure in the compression chamber is low while preventing the refrigerant volume from decreasing, so the injection pressure can be set low, increasing the injection flow rate and sufficiently improving the heating capacity of the air conditioner. can do.

According to a second aspect of the present invention, there is provided a scroll compressor in which gas injection is performed to a compression chamber between a fixed scroll and an orbiting scroll through an injection port. The width of the tip seal between the fixed scroll and the fixed scroll is substantially the same.

In such a configuration, the diameter of the injection port is substantially the same as the width of the tip seal, so that the injection port straddles the tip seal of the wrap and separates the two compressions formed by the tip seal and the wrap. By increasing the diameter of the injection port to approximately the same size as the width of the tip seal while eliminating the inconvenience of reducing the efficiency of the compressor through both chambers, the flow path resistance to gas refrigerant during injection is reduced. In addition, the injection flow rate can be increased, and the heating capacity of the air conditioner can be improved.

According to a third aspect of the present invention, there is provided a scroll compressor in which a gas refrigerant is injected into a compression chamber between a fixed scroll and an orbiting scroll through an injection port. It is characterized by having been made larger than that.

In such a configuration, the wrap thickness of the orbiting scroll can be increased, so that the diameter of the injection port can be increased, and the injection end diameter can be reduced while keeping the diameter of the injection port unchanged. The pressure of the compression chamber is low and the injection pressure can be reduced.

[0015] For this reason, the injection flow rate can be increased, and the heating capacity of the air conditioner can be improved.
In addition, by making the orbiting scroll wrap thicker, even if it is made of aluminum etc. that is weak in strength, the bending strength is improved, it prevents falling down during processing and use, and exhibits stable heating performance for a long time be able to.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some embodiments of the present invention will be described below with reference to FIGS.

(Embodiment 1) Embodiment 1 is a case of a horizontally installed scroll compressor for refrigeration and air conditioning.
Shows the overall configuration.

To explain this, in a closed container 1, a scroll type compression mechanism 2 is provided at one end, an electric motor 3 for driving the compression mechanism 2 is provided at an intermediate portion, and an oil 4 as a lubricant is provided at the other end. And an oil pump 6 for sending out the oil 4 in the oil reservoir 5 to the lubrication target portion. The oil pump 6 can be replaced with various types used in this type of refrigeration system.

The compression mechanism 2 comprises a fixed scroll 11 and an orbiting scroll 12 which are engaged with each other in the same manner as in the prior art. By driving the orbiting scroll 12 to orbit, several compression chambers 13 are formed between them. Suction port 1 shown in 2
The compression is performed by reducing the volume while moving from the outer peripheral side to the inner peripheral side to the discharge port 15.

The support and drive and the guide structure for the fluid that is sucked, compressed and discharged may be configured in any manner. In the first embodiment, the compression mechanism 2 engages the inner scroll 12 with the fixed scroll 11 fixed to one end, and the orbiting scroll 12 is fixed to the fixed scroll 11 in correspondence with the horizontal installation type. Main bearing member 19 bolted to scroll 11 and integrated
It is to be sandwiched between. The electric motor 3 includes an annular stator 3a fixed to the inner surface of the closed casing 1 and a rotor 3b disposed inside the stator 3a. A crankshaft 16 for orbiting the orbiting scroll 12 of the compression mechanism 2 is provided on the rotor 3b.
Is fixed.

The crankshaft 16 is supported by a sub-bearing member 17 on the other end side of the closed casing 1, and the main shaft 1 on the opposite side.
8 is carried in the closed casing 1 by a main bearing member 19. The auxiliary bearing member 17 and the main bearing member 19 have a rolling bearing 21 and a sliding bearing 22 for the bearing. The main shaft 18 is connected to the orbiting scroll 1 via the eccentric bearing 23.
When the main shaft 18 is rotated, the orbiting scroll 12 is turned by the function of an Oldham ring 28 provided between the main bearing member 19 and the orbiting scroll 12 when the main shaft 18 is rotated. However, the bearing structure as described above can be variously modified. The oil pump 6 is attached to the auxiliary bearing member 17.

Since the first embodiment is a scroll compressor for refrigeration and air conditioning, suction by a compression mechanism 2 is performed.
The fluid that is compressed and discharged is a refrigerant, and the oil 4 is compatible with the fluid.

A gas suction pipe 32 is connected to the suction port 14, and a discharge chamber 33 in the closed container 1 is connected to the discharge port 15.
The gas discharge pipe 34 is connected via the.

The oil pump 6 is driven by the crankshaft 16 together with the compression mechanism 2, sends out the oil 4 in the oil reservoir 5 into an oil passage 35 formed vertically through the crankshaft 16, and first supplies the oil to the eccentric bearing 23. A part of the oil 4 after being supplied to the eccentric bearing 23 is supplied to the sliding bearing 22 and the compression mechanism 2 through each gap, and the rest is returned to the lower oil reservoir 5 through the passage 36.

The refrigerant sucked into the compression mechanism 2 and compressed and discharged is brought into contact with the compatible oil 4 in the compression mechanism 2 or the like to accompany the same, and the oil is transported to a further detail and required. Achieve lubrication.

Further, the discharge port 15 is provided with a check valve 42 for preventing the orbiting scroll 12 from rotating backward when the compression mechanism 2 is stopped, and a check valve guide 43 for regulating the movement of the orbiting scroll 12. .

A condenser 44, a capillary tube 45, a gas-liquid separator 46, a capillary tube 47, and an evaporator 48 are sequentially connected between the gas discharge pipe 34 and the gas suction pipe 32. The entire refrigerating cycle including the compression mechanism 2 is annularly connected. Although a non-heat pump type is shown for simplicity of description, a heat pump type refrigeration cycle may be configured.

The fixed scroll 11 is provided with two injection ports 51 for performing gas injection into the compression chamber 13 as shown in FIGS. An injection pipe 52 is connected to each injection port 51, and a gas refrigerant supply pipe 53 from the gas-liquid separator 46 is connected to each injection pipe 52. As a result, the gas refrigerant separated into gas and liquid by the gas-liquid separator 46 is injected into the compression chamber 13 through the refrigerant supply pipe 53, and the efficiency of the compressor in the compression mechanism 2 is increased. I do.
Note that this gas injection may be performed in a timely manner according to the operation state of the refrigeration system, and in order to control this,
An electromagnetic valve 55 is provided in the middle of the refrigerant supply pipe 53, so that the opening and closing of the refrigeration system is controlled as needed. This control can be performed by a microcomputer together with the operation control of the refrigerating apparatus, for example, but is not limited to this.

In the first embodiment, in particular, the injection is started before the compression chamber sucks the refrigerant and is closed. For example, the injection port 51 is located at a position as shown in FIGS. Is provided. 2 (a) to 2 (c) show that the gas refrigerant is sucked and compressed in the compression chamber 13.
The state change at the time of ejection is sequentially shown.

FIG. 2A shows a state in which the compression chamber 13 located closest to the suction port 14 is about to finish the suction of the gas refrigerant, and the injection port 51 is formed by the end face of the wrap 12 a of the orbiting scroll 12. To be precise, it is closed by a tip seal (not shown) for sealing between the fixed scroll 11 provided on the end face. Therefore, gas injection into the compression chamber 13 is not performed.

FIG. 2B shows a state in which the compression chamber 13 is about to be closed as shown in FIG. 2B-2, and the injection port 51 is shown in FIG. 2B-1.
As shown in FIG. 7, the orbiting scroll 12 is about to be opened by further turning.

FIG. 2C shows a state where the compression chamber 13 is closed as shown in FIG. 2C-2, and an injection port 51 is provided as shown in FIG. 2C-1. It is already open, and gas injection through the gas refrigerant supply pipe 53 is already performed before the compression chamber 13 is closed.

As described above, if the injection is performed before the compression chamber 13 sucks the gas refrigerant and is closed, the compression chamber 13 is still at a low pressure, and thus the pressure is obtained by the gas-liquid separator 46 or the pressure control operation is performed. As a result, the injection flow rate for a given injection pressure is increased, and a sufficient injection flow rate can be obtained even at a low pressure, so that the heating capacity can be sufficiently improved. In addition, since the injection timing is such that the compression chamber 13 is closed immediately after the start of the gas injection as shown in FIG. 2C-2, the injected gas refrigerant does not flow backward to the suction port 14 side, and the compression mechanism 2 can be prevented from lowering in efficiency.

The compression chamber 1 is rotated by three rotations of the crankshaft 16.
FIG. 3 shows a specific relationship between the pressure change of the refrigerant and the injection timing when suction, compression, and discharge are performed by No. 3.

Referring to FIG. 3, three injection start points T ₁ , T ₂ and T ₃ are considered for the suction pressure P _IN and the discharge pressure P _OUT . T ₁ is a time point when no compression is performed before the compression chamber 13 is closed, T ₂
The compression start time, T ₃ is the time when the compression chamber pressure is slightly elevated from the suction pressure P _IN little willing compression. The injection end points T ₁ ′, T ₂ ′ and T ₃ ′ are determined by the diameter and position of the injection port, and correspond to the injection start points T ₁ , T ₂ and T ₃ respectively.
Then, the injection end time T ₁ ′,
It is necessary to set the injection pressure higher than the pressures P ₁ , P ₂ , and P ₃ at T ₂ ′ and T ₃ ′. To set the injection pressure lower, the injection start time must be set at the time of the first embodiment. Thus, it is preferable to set before the compression chamber is closed. The range is up to a crank angle of −60 ° due to the geometrical structure, the passage area to the suction chamber side is small, and there is no influence by the backflow. Therefore, the injection timing is set to the compression chamber 1 as in the first embodiment.
Preferably, it is set before 3 is closed.

(Embodiment 2) In Embodiment 2, as shown in FIG. 4, a tip seal between the diameter D of the injection port 51 and the fixed scroll 11 provided on the end face of the wrap 12a of the orbiting scroll 12 is shown. The third embodiment differs from the first embodiment in that the width B is substantially the same as the width B of the first embodiment. Since other configurations are the same as those in the first embodiment, the same members are denoted by the same reference numerals, and overlapping illustration and description are omitted.

According to this, the injection port 5
By increasing the width of the chip seal 61 to substantially the same size as the width B of the tip seal 61, the flow resistance at the time of gas injection can be reduced, the injection flow rate can be increased, and the heating capacity can be improved. Moreover, the diameter D of the injection port 51 is equal to the thickness B of the tip seal 61.
In this case, the injection port 51 straddles the wrap 12a and communicates with both the tip seal 61 and the two compression chambers 13 partitioned by the wrap 12a, thereby reducing the efficiency of the compression mechanism 2. Can be eliminated.

Accordingly, the injection port 5
The diameter D of the injection seal 51 is set large so as to exceed the width B of the tip seal 61 and reach the wrap 11a so as to be advantageous for increasing the injection flow rate.
The structure is such that the efficiency of the compression mechanism 2 does not decrease over the two compression chambers 13 partitioned by 2a.

The minute gap Δ shown in FIG. 4 is a gap in units of microns and is negligible in consideration of a reduction in the efficiency of the compression mechanism 2.

Although the second embodiment employs the injection timing of the first embodiment, the injection port 5 does not have such a feature.
As the diameter of 1 increases without causing a decrease in the efficiency of the compression mechanism 2, the injection flow rate can be increased and the heating capacity can be improved, and such a thing also belongs to the category of the present invention.

(Embodiment 3) In Embodiment 3, as shown in FIG. 5, the orbiting scroll 12 according to Embodiment 2 is used.
With the difference that is larger than the thickness T ₁₁ of the thickness T ₁₂ of the wrap 12a wrap 11a of the fixed scroll 11. Other configurations and operational effects are the same as those of the second embodiment. Therefore, the same members are given the same reference numerals,
Overlapping illustrations and descriptions are omitted.

As described above, in the third embodiment, by utilizing the fact that the wrap thickness T ₁₂ of the orbiting scroll 12 is larger than the wrap thickness T ₁₁ of the fixed scroll 11, the injection port diameter D is changed to the orbiting scroll 12. Wrap thickness T
Increase the injection flow rate by increasing to ₁₂ cups to increase the heating capacity. In addition, the injection port 51 extends over the wrap 12a of the orbiting scroll 12 and communicates with both of the two compression chambers 13 partitioned by the wrap 12a.
It is possible to avoid a decrease in the efficiency of the system. Moreover, the wrap 12a of the orbiting scroll 12 is fixed to the fixed scroll 11
Since the thickness is larger than the wrap 11a, the bending strength is improved, so that plastic collapse during processing or use is prevented,
A stable heating function can be exhibited over a long period of time. Further, in the third embodiment, since the thickness of the wrap 12a of the orbiting scroll 12 is increased, when the diameter D of the injection port is not increased, the range in which the injection port 51 is closed by the wrap 12a of the orbiting scroll 12 is expanded. The opening range of the injection port 51 is narrowed, the injection end angle can be reduced, the compression chamber pressure at the end of the injection can be set low, and the injection pressure can be set low.
The injection flow rate increases and the heating capacity increases.

[0043]

According to the first aspect of the present invention, the injection is performed when the pressure is low before the compression chamber sucks the refrigerant and is closed, thereby increasing the injection flow rate and sufficiently improving the heating capacity. be able to. Moreover,
By selecting the injection timing at which the compression chamber is closed immediately after the start of the injection, the injected gas refrigerant does not flow backward to the suction port side, so that the efficiency of the compressor can be prevented from lowering.

According to the second aspect of the present invention, the diameter of the injection port is increased to a diameter substantially equal to the width of the tip seal, so that the flow resistance to the gas refrigerant at the time of injection is reduced, thereby increasing the injection flow rate and heating. Ability to improve. In addition, since the diameter of the injection port is substantially the same as the thickness of the tip seal, the injection port straddles the tip seal of the lap and communicates with both of the two compression chambers partitioned by the tip seal and the lap. The inconvenience that lowers the efficiency of the machine can be solved.

According to the third aspect of the present invention, by utilizing the fact that the wrap thickness of the orbiting scroll is larger than the wrap thickness of the fixed scroll, the injection port diameter is increased to the full wrap thickness of the orbiting scroll and the injection flow rate is increased. If the diameter of the injection port is not increased to increase the wrap thickness of the orbiting scroll and increase the wrap thickness of the orbiting scroll, the injection port opening range is narrowed, the injection end point can be set earlier, and the injection pressure can be set lower, increasing the heating capacity. I do. In addition, it is possible to prevent the injection port from straddling the wrap of the orbiting scroll and communicating with both of the two compression chambers, thereby reducing the efficiency of the compressor. Moreover,
The wrap of the orbiting scroll has a larger bending strength than that of the fixed scroll, so that the plastic wrap during working or use can be prevented, and a stable heating function can be exhibited over a long period of time.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram showing an injection state of the compressor of FIG.

3 is a graph showing the relationship between the progress of compression (crankshaft rotation angle) in the compression chamber of the compressor of FIG. 1 and the pressure in the compression chamber, and the injection timing.

FIG. 4 is a partial cross-sectional view showing Embodiment 2 of the present invention.

FIG. 5 is a partial cross-sectional view showing Embodiment 3 of the present invention.

[Explanation of symbols]

2 Compression mechanism 11 Fixed scroll 11a Wrap 12 Orbiting scroll 12a Wrap 13 Compression chamber 14 Suction port 15 Discharge port 51 Injection port 61 Chip seal B Chip seal width D Injection port diameter T ₁₁ Fixed scroll wrap thickness T ₁₂ Orbited scroll wrap thickness

Claims (3)

[Claims] 1. A scroll compressor in which gas is injected into a compression chamber between a fixed scroll and an orbiting scroll through an injection port, wherein injection is started before the compression chamber sucks refrigerant and is closed. A scroll compressor characterized by providing an injection port in the scroll compressor. 2. A scroll compressor in which gas injection is performed through a injection port into a compression chamber between a fixed scroll and an orbiting scroll. A scroll seal having a width substantially equal to a width of a chip seal between the scroll compressor and the scroll compressor. 3. A scroll compressor in which gas is injected into a compression chamber between a fixed scroll and an orbiting scroll through an injection port, wherein the wrap thickness of the orbiting scroll is made larger than the wrap thickness of the fixed scroll. Features scroll compressor.