JP4156951B2 - Hybrid compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a hybrid compressor in which a first compression mechanism driven only by a first drive source and a second compression mechanism driven only by a second drive source are integrally assembled.
[0002]
[Prior art]
Conventionally, a hybrid compressor having a single compression mechanism that can be driven by a vehicle engine or a built-in electric motor is known (Patent Document 1). For example, when the engine is stopped during driving by the engine, switching to driving by the built-in electric motor is performed.
[0003]
However, in a conventional hybrid compressor, since a single compression mechanism is selectively switched between an engine with a different output and a built-in electric motor, it is difficult to drive both drive sources with optimum efficiency. is there. Further, pulsation at the time of discharge may occur.
[0004]
Such a conventional hybrid compressor is still in an unpublished stage of application. However, the applicant of the present invention uses only a scroll-type first compression mechanism driven only by a vehicle engine and an electric motor. A hybrid compressor has been proposed in which both fixed scrolls with a driven scroll-type second compression mechanism are integrally assembled back to back so that the first compressor and the second compressor can be selectively or simultaneously driven. (Patent Document 2).
[0005]
However, in each of the first compression mechanism that is driven by an engine having a large output and the second compression mechanism that is driven by an electric motor having an output smaller than that of the engine, an attempt is made to balance and optimize the suction capacity and the discharge capacity. Therefore, it is necessary to set the amount of fluid sucked by the first compression mechanism to be larger (for example, about twice) than the amount of suction of the second compression mechanism. Further, in order to suppress the pressure loss during discharge, it is necessary to set the cross-sectional area of the discharge passage to be large (for example, to have a large diameter) in accordance with the discharge flow rate on the first compression mechanism side where the suction amount is large.
[0006]
For this reason, when the fixed scrolls of both compression mechanisms are arranged back to back and the discharge passages of the compression mechanisms are formed between the fixed scrolls of the compression mechanisms, the cross-sectional area of the discharge passages extending from the first compression mechanism to the discharge chamber is determined. Therefore, it is necessary to set the dimension between the two fixed scrolls. Therefore, there is a risk of extending the axial dimension of the compressor itself. In addition, when the fixed scrolls of both compression mechanisms are integrally formed with one fixed scroll member with such a structure, the fixed scroll member becomes thick and may not be able to meet the demand for weight reduction of the device. . In recent years, in the field of vehicle air conditioners, the installation space has been narrowed, and the compressor 1 itself has been required to be downsized, particularly in the axial direction.
[0007]
[Patent Document 1]
Japanese Unexamined Patent Publication No. 2000-130323 (2nd page, FIG. 2)
[0008]
[Patent Document 2]
Japanese Patent Application No. 2002-031664 (Fig. 1)
[0009]
[Problems to be solved by the invention]
The object of the present invention is to focus on the problems of the conventional hybrid compressor as described above, and on the premise of the previous proposal by the applicant, the device is further reduced in size and weight, and the installation space is reduced. It is to provide a hybrid compressor that can be manufactured at low cost.
[0010]
[Means for Solving the Problems]
In order to solve the above problems, a hybrid compressor according to the present invention includes a scroll-type first compression mechanism driven only by a first drive source and a scroll-type second compression mechanism driven only by a second drive source. Is a hybrid compressor in which the fixed scrolls of both compression mechanisms are integrally assembled so as to be arranged back to back, and independent discharge passages are provided from both compression mechanisms to the discharge chamber of the compressor, The cross-sectional area of the discharge passage from the compression mechanism to the discharge chamber is larger than the cross-sectional area of the discharge passage from the other compression mechanism to the discharge chamber.
[0011]
The fixed scrolls of both the compression mechanisms can be formed back to back and integrally, for example, from a single fixed scroll member. If the fixed scrolls of both compression mechanisms are formed back to back and integrally, the size of the compressor in the axial direction can be shortened, contributing to downsizing of the apparatus. Further, the reduction of the number of parts can promote the weight reduction of the apparatus and the reduction of the manufacturing cost. Furthermore, if a discharge passage is formed between the two fixed scrolls, it is possible to further promote downsizing of the apparatus in the axial direction.
[0012]
The passage having a large cross-sectional area may be formed as a single discharge passage, but may be formed from a plurality of discharge passages. If a plurality of discharge passages are arranged at an angle in the circumferential direction of the compressor between the two fixed scrolls, the dimension between the two fixed scrolls and the axial dimension of the compressor can be increased even if the sectional area of the discharge passage is increased. Can be shortened. Also, when forming from a single discharge passage, for example, if the cross-sectional shape is formed in an oval shape extending in the circumferential direction of the compressor, the axial dimension of the compressor can be shortened in the same manner.
[0013]
Further, when a discharge passage having a large cross-sectional area is formed from a plurality of discharge passages, the discharge holes of each discharge passage can be simultaneously opened and closed by one discharge valve. For example, if the plurality of discharge passages are arranged at different angles in the circumferential direction of the compressor, the discharge holes are also arranged in the direction, so that each discharge hole can be opened and closed simultaneously using a single valve (for example, a reed valve). It becomes possible to do.
[0014]
Further, the discharge hole of the discharge passage having a large cross-sectional area and the discharge hole of the other discharge passage can be substantially opened and closed by different operations of one discharge valve. For example, the discharge hole of the discharge passage having a large cross-sectional area may be opened and closed on one end side of the reed valve, and the discharge hole of the other discharge passage may be opened and closed on the other end side of the reed valve. Thus, by using a common discharge valve and reducing the number of parts, an increase in the number of parts can be prevented, and cost reduction can be achieved while improving assembly workability.
[0015]
The first drive source and the second drive source are not particularly limited, and examples of the first drive source include a vehicle prime mover. On the other hand, examples of the second drive source include an electric motor built in the compressor. In addition, the motor | power_engine for vehicles in this specification is the concept containing the engine for vehicle travel which consists of an internal combustion engine, and the electric motor for vehicle travel in an electric vehicle.
[0016]
Since the electric motor as the second drive source is built in the compressor, it is preferably small. For this reason, torque is small compared with the motor | power_engine for vehicles. Therefore, it is preferable to set the maximum discharge flow rate of the first compression mechanism driven by the vehicle prime mover as the first drive source to be larger than the maximum discharge flow rate of the second compression mechanism. In this case, the discharge passage having a large cross-sectional area is a discharge passage extending from the first compression mechanism to the discharge chamber.
[0017]
In the hybrid compressor as described above, an independent discharge passage is provided for each compression mechanism, and one discharge passage has a larger cross-sectional area than the other discharge passage. That is, in the hybrid compressor as described above, even if there is a difference in the maximum discharge flow rate of each compression mechanism, the cross-sectional area of the corresponding discharge passage is set according to this difference, so that pressure loss can be effectively prevented. . For example, pressure loss can be reliably prevented by setting the cross-sectional area of the discharge passage on the compression mechanism side having a large maximum discharge flow rate to be larger than the cross-sectional area of the discharge passage on the compression mechanism side having a small maximum discharge flow rate. Further, if the discharge passage is formed as a plurality of discharge passages arranged at different angles in the circumferential direction between the two fixed scrolls, or the cross section of the discharge passage is formed in an oval shape extending in the circumferential direction of the compressor In addition, it is possible to increase only the cross-sectional area of the discharge passage while suppressing or extending the extension of the axial dimension of the compressor.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, preferred embodiments of the hybrid compressor of the present invention will be described with reference to the drawings.
1 to 4 show a hybrid compressor according to a first embodiment of the present invention. In the figure, reference numeral 1 denotes a hybrid compressor. The hybrid compressor 1 has a front housing 2 and a rear housing 3. Between the front housing 2 and the rear housing 3, there is provided a fixed scroll member 6 constituting a fixed scroll of both the scroll type first compression mechanism 4 and the scroll type second compression mechanism 5. The front housing 2, the fixed scroll member 6, and the rear housing 3 are fastened by through bolts 56. In this embodiment, the fixed scrolls of the compression mechanisms 4 and 5 are formed back to back and integrally as shown in FIGS.
[0019]
A cup-shaped suction chamber and a discharge chamber forming member 9 for forming the suction chamber 7 and the discharge chamber 8 are joined to the outer peripheral surface of the fixed scroll member 6. The suction chamber 7 and the discharge chamber 8 are formed as a space surrounded by the outer peripheral surface of the fixed scroll member 6 and the forming member 9. A wall 10 is provided inside the forming member 9, and the suction chamber 7 and the discharge chamber 8 are partitioned by the wall 10.
[0020]
The fixed scroll member 6 is provided with a suction hole 11 that communicates the suction chamber 7 with the inside of the compressor 1. A plurality of suction holes 11 are arranged in the circumferential direction of the fixed scroll member 6, in other words, in the circumferential direction of the compressor 1.
[0021]
A first discharge passage 12 extending from the first compression mechanism 4 to the discharge chamber is provided inside the fixed scroll member 6. The first discharge passage 12 is formed of two discharge passages 13 and 14 as shown in FIGS. The discharge passages 13 and 14 forming the first discharge passage 12 are communicated with the discharge chamber 8 through the discharge holes 15 and 16. The discharge passages 13 and 14 are arranged at an angle in the circumferential direction of the compressor 1. A second discharge passage 17 extending from the second compression mechanism 5 to the discharge chamber 8 is provided inside the fixed scroll member 6. The second discharge passage 17 communicates with the discharge chamber 8 through the discharge hole 18.
[0022]
In the present embodiment, the first compression mechanism 4 is driven only by the vehicle prime mover 19, and the second compression mechanism 5 is driven only by the electric motor 20 built in the compressor 1. The maximum discharge capacity of both compression mechanisms 4 and 5 is set to be larger in the first compression mechanism 4 than in the second compression mechanism 5. For this reason, from the viewpoint of preventing pressure loss, the cross-sectional area of the first discharge passage 12 formed by the plurality of discharge passages 13 and 14 is set larger than the cross-sectional area of the second discharge passage 17.
[0023]
In the discharge chamber 8, a reed valve 21 is provided as a discharge valve that can open and close the discharge holes 15, 16, and 18. As shown in FIG. 4, the reed valve 21 can simultaneously open and close the discharge holes arranged in the circumferential direction of the compressor 1. Specifically, the discharge holes 15 and 16 are opened and closed by one end side 24 of the reed valve 21, and the discharge hole 18 is opened and closed by the other end side 25. That is, in the present embodiment, the discharge holes 15 and 16 and / or the discharge hole 18 are opened and closed by the operation of different parts of the single reed valve 21. The reed valve 21 is fixed to the fixed scroll member 6 by bolts 23 together with a retainer 22 that regulates the lift amount of the valve 21.
[0024]
The first compression mechanism 4 includes a fixed scroll 27 including a fixed scroll member 6 and a spiral wound body 26 formed integrally with the fixed scroll member 6, an end plate 28, and a spiral formed integrally with the end plate 28. A movable scroll 30 including a winding body 29 is provided. The spiral body 26 of the fixed scroll 27 and the spiral body 29 of the movable scroll 30 are engaged with each other at an angle.
[0025]
The main shaft (drive shaft) 31 is disposed substantially in the horizontal direction (left-right direction in FIG. 1), and the hybrid compressor 1 of this embodiment is configured as a horizontal compressor. A crank mechanism 32 is formed at one end of the main shaft 31. The crank pin 33 of the crank mechanism 32 is provided at a position eccentric from the axis of the main shaft 31 and is inserted and fitted to the eccentric bush 34 with a certain play amount. The eccentric bush 34 is rotatably inserted into a drive bearing 35 inserted into the protrusion of the movable scroll 30. The other end of the main shaft 31 is provided with an electromagnetic clutch 36 that transmits power from the vehicle prime mover 19 as a first drive source to the main shaft. The prime mover 19 and the electromagnetic clutch 36 are connected via a pulley 37.
[0026]
The electromagnetic clutch 36 includes a clutch armature 38 fixed to the main shaft 31, and an electromagnet 39 that attaches and detaches the pulley 37 and the clutch armature 38 to turn the clutch 36 on and off.
[0027]
In the present embodiment, when the power from the vehicle running prime mover 19 that drives only the first compression mechanism 4 is transmitted to the main shaft 31 via the electromagnetic clutch 36, the eccentric bush into which the crank pin 33 is inserted and fitted. 34 rotates. Along with this, a turning motion is applied to the movable scroll 30 whose rotation is prevented by the ball coupling 40 as the rotation prevention mechanism.
[0028]
The fluid (for example, refrigerant) sucked into the hybrid compressor 1 from the suction hole 11 as the movable scroll 30 rotates is taken into the spiral body from the outer ends of the spiral bodies 26 and 29. Then, as the fluid pocket formed by the spiral bodies 26 and 29 is moved toward the center while reducing its volume, the fluid is compressed, and the hole 60 formed in the fixed scroll member 6, It flows out from the one discharge passage 12 to the high-pressure side of the external circuit through the discharge chamber 8 disposed at a position above both the compression mechanisms 4 and 5.
[0029]
On the other hand, the second compression mechanism 5 is formed integrally with the fixed scroll 42 including the fixed scroll member 6 and the spiral body 41 formed integrally with the fixed scroll member 6, the end plate 43, and the end plate 43. A movable scroll 45 including a spiral body 44 is provided. In the present embodiment, the fixed scrolls 27 and 42 of the compression mechanisms 4 and 5 are integrally formed with the scroll member 6, and the fixed scrolls 27 and 42 are arranged back to back. Therefore, the enlargement of the main shaft 31 of the hybrid compressor 1 in the axial direction is suppressed, and the compactness as a horizontal compressor is achieved.
[0030]
A crank mechanism 47 is formed at one end of the drive shaft 46. The crank pin 48 of the crank mechanism 47 is provided at a position that is eccentric from the axis of the drive shaft 46, and is inserted and fitted to the eccentric bush 49 with a certain play amount. The eccentric bush 49 is rotatably inserted into a drive bearing 50 provided in the protrusion of the movable scroll 45. In the present embodiment, the second drive source that drives only the second compression mechanism 5 includes an electric motor 20 built in the compressor 1. When the power from the electric motor 20 is transmitted to the rotor 52 fixed to the drive shaft 46, the eccentric bush 49 into which the crank pin 48 is inserted and fitted rotates. Along with this, a turning motion is applied to the movable scroll 45 whose rotation is blocked by the ball coupling 53 as a rotation blocking mechanism. A connector 54 is connected to the electric motor 20. Reference numeral 55 denotes a stator of the electric motor 20.
[0031]
The fluid that has flowed into the compressor 1 from the suction hole 11 as the movable scroll 45 turns is swirled from the outer ends of the two spiral bodies 41, 44 engaged with each other by shifting the angle of the second compression mechanism 5. Captured inside. Then, the fluid pocket formed by the spiral bodies 41 and 44 is compressed as it moves toward the center while reducing its volume, and the hole 61 formed in the fixed scroll member 6, the second discharge It is sent from the passage 17 to the discharge chamber 8.
[0032]
In the hybrid compressor as in the present embodiment, independent discharge passages 12 and 17 are provided in the compression mechanisms 4 and 5, respectively, and the first discharge on the side of the first compression mechanism 4 having a large maximum discharge flow rate. The cross-sectional area of the passage 12 is set larger than the cross-sectional area of the second discharge passage 17 on the second compression mechanism 5 side where the maximum discharge flow rate is small. That is, since the cross-sectional areas of the discharge passages 12 and 17 are set in accordance with the maximum discharge flow rate of the compression mechanisms 4 and 5, it is possible to effectively prevent pressure loss during discharge.
[0033]
Further, the cross-sectional area of the first discharge passage 12 is set to be larger than the cross-sectional area of the second discharge passage 17, which is arranged so that the first discharge passage 12 is shifted in the circumferential direction of the compressor 1. Therefore, even if the cross-sectional area of the first discharge passage 12 is increased, the dimension between the fixed scrolls 24 and 42 (thickness dimension A of the fixed scroll member 6) is achieved. The axial dimension of the compressor 1 itself is not extended. Moreover, the thickness dimension A of the fixed scroll member 6 is shortened without changing the axial dimension of the compressor 1, whereby the apparatus can be reduced in size and weight. In addition, a sufficient storage space in the compressor axial direction of the electric motor 20 can be secured. For example, in order to shorten the dimension of the compressor in the axial direction, the diameter of the electric motor 20 is reduced to about 2 mm only by trying to reduce the dimension of the electric motor 20 in the above direction while maintaining the torque of the electric motor 20. It increases by 10 mm and the weight increases by 300 g. However, in this embodiment, a sufficient installation space for the electric motor 20 can be secured, and there is no need to forcibly reduce the size of the electric motor 20. Therefore, the hybrid compressor 1 can be reduced in size while preventing the above-described adverse effects. It is possible to reduce the weight.
[0034]
Further, in the present embodiment, the discharge holes 15, 16, 18 are opened and closed by the reed valve 21 as one discharge valve, so that the number of discharge passages increases, thereby increasing the number of discharge holes. An increase in the number of parts can be prevented.
[0035]
5 and 6 show a hybrid compressor according to the second embodiment of the present invention. In addition, the same number is attached | subjected to the member same as the said 1st embodiment, and the description is abbreviate | omitted. In the present embodiment, the first discharge passage 12 of the first compression mechanism 4 is formed as a discharge passage 57 having an oval cross-sectional shape. The cross-sectional shapes of the discharge passage 57 and the discharge hole 58 are formed in an oval shape extending in the circumferential direction of the fixed scroll member 6 and in the circumferential direction of the hybrid compressor. As shown in FIGS. 5 and 6, the cross-sectional area of the first discharge passage 12 is larger than the cross-sectional area of the second discharge passage 17.
[0036]
Further, the discharge hole 58 of the first discharge passage 12 is opened and closed by one end side 24 of the reed valve 21. Further, the discharge hole 18 of the second discharge passage 17 is opened and closed by the other end side 25 of the reed valve 21.
[0037]
Also in this embodiment, the cross-sectional area of the first discharge passage 12 of the first compression mechanism 4 having a large maximum discharge flow rate can be increased while the thickness of the fixed scroll member 6 is kept as it is or is reduced. The pressure loss can be prevented while the extension of the axial dimension of the machine is prevented or suppressed. In addition, the apparatus can be further reduced in size and weight. Further, the number of parts can be prevented from increasing by opening and closing the plurality of discharge holes 18 and 58 with one reed valve 21.
[0038]
【The invention's effect】
As described above, when the hybrid compressor of the present invention is used, the pressure loss can be reduced, the apparatus can be reduced in size and weight, and the apparatus can be flexibly responded to a request for narrowing the installation space of the apparatus. .
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a hybrid compressor according to a first embodiment of the present invention.
FIG. 2 is a plan view of a fixed scroll member of the hybrid compressor of FIG.
3 is an enlarged longitudinal sectional view of a fixed scroll member of the hybrid compressor of FIG. 1. FIG.
4 is a cross-sectional view of a discharge chamber of the hybrid compressor in FIG. 1. FIG.
FIG. 5 is a plan view of a fixed scroll member of a hybrid compressor according to a second embodiment of the present invention.
6 is a cross-sectional view of a discharge chamber of the hybrid compressor of FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Hybrid compressor 2 Front housing 3 Rear housing 4 1st compression mechanism 5 2nd compression mechanism 6 Fixed scroll member 7 Suction chamber 8 Discharge chamber 9 Suction chamber, discharge chamber formation member 10 Wall 11 Suction hole 12 First discharge passage 13, 14, 57 Discharge passages 15, 16, 18, 58 forming the first discharge passage 17 Discharge hole 17 Second discharge passage 19 Motor for vehicle 20 Electric motor 21 Reed valve 22 Retainer 23 Bolt 24 One end side 25 of reed valve Valve other end side 26, 29, 41, 44 Spiral winding body 27, 42 Fixed scroll 28, 43 End plate 30, 45 Movable scroll 31 Main shaft (drive shaft)
32, 47 Crank mechanism 33, 48 Crank pin 34, 49 Eccentric bush 35, 50 Drive bearing 36 Electromagnetic clutch 37 Pulley 38 Clutch armature 39 Electromagnet 40, 53 Ball coupling 46 Drive shaft 52 Rotor 54 Connector 55 Stator 56 Through bolt 60, 61 Hole A Fixed scroll member thickness dimension

Claims (8)

The scroll-type first compression mechanism driven only by the first drive source and the scroll-type second compression mechanism driven only by the second drive source are arranged such that the fixed scrolls of both compression mechanisms are arranged back to back. A hybrid compressor that is assembled integrally and has independent discharge passages from both compression mechanisms to the discharge chamber of the compressor, and the cross-sectional area of the discharge passage from one compression mechanism to the discharge chamber is the compression of the other A hybrid compressor characterized by being larger than a cross-sectional area of a discharge passage from a mechanism to a discharge chamber. The hybrid compressor according to claim 1, wherein the fixed scrolls of both the compression mechanisms are formed back to back and integrally. The hybrid compressor according to claim 1 or 2, wherein the discharge passage having a large cross-sectional area is formed as a plurality of discharge passages. The hybrid compressor according to claim 3, wherein the discharge holes to the discharge chambers of the plurality of discharge passages are simultaneously opened and closed by one discharge valve. The hybrid compressor according to claim 1 or 2, wherein the discharge passage having a large cross-sectional area is formed into a passage having an elliptical cross-sectional shape. The hybrid compressor according to any one of claims 1 to 5, wherein the first drive source comprises a vehicle prime mover, and the second drive source comprises an electric motor built in the compressor. The maximum discharge flow rate of the first compression mechanism driven by the vehicle prime mover is larger than the maximum discharge flow rate of the second compression mechanism driven by the electric motor, and the disconnection from the first compression mechanism to the discharge chamber is performed. The hybrid compressor according to claim 6, wherein a discharge passage having a large area is provided. The discharge hole to the discharge chamber of the discharge passage having the large cross-sectional area and the discharge hole to the discharge chamber of the other discharge passage are substantially opened and closed by operation of different portions of one discharge valve. The hybrid compressor in any one of.

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