CN101230872B - Compressor and constant speed joint - Google Patents
Compressor and constant speed joint Download PDFInfo
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- CN101230872B CN101230872B CN2008100813919A CN200810081391A CN101230872B CN 101230872 B CN101230872 B CN 101230872B CN 2008100813919 A CN2008100813919 A CN 2008100813919A CN 200810081391 A CN200810081391 A CN 200810081391A CN 101230872 B CN101230872 B CN 101230872B
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Abstract
The invention provides a swash plate compressor or a swing swash plate compressor with improved reliability, by keeping a good lubrication state of a sliding part between a swash plate and a shoe or a sliding part of a detent mechanism. The swing swash plate compressor comprises: a drive shaft; a swirl plate; a swing swash plate whose rotation is prevented by the detent mechanism; a piston; and a center shaft. The swing swash plate compressor has a device separating oil in refrigerant gas, and a high-pressure oil storage chamber storing the separated oil, and an oil guide passage is disposed to the center shaft to directly supply oil to the sliding part of the detent mechanism from the high-pressure oil storage chamber. In the swing swash plate compressor, an oil guide passage(s) is/are disposed to the drive shaft and/or a cylinder block, and the oil from the high-pressure oil storage chamber 122 is directly supplied to the sliding part between the swash plate and the shoe.
Description
Technical field
The present invention relates to a kind of compressor that is used for the refrigeration agent of minimum cylinder volume formula pump or air-conditioning system; Especially relate to a kind of oblique tray type compressor, constant velocity universal joint and swashplate type compressor, it is suitable for being used for like bus, the jumbo swashplate type variable conpacitance compressor of needs.
Background technique
As correlation technique, utilize the rotation-preventing mechanism of the swing swash plate of forming by constant velocity universal joint (swing disc) and be well-known the structure that this rotation-preventing mechanism is arranged in the center of swinging swash plate.In this case, constant velocity universal joint adopts grease lubrication usually, but when being used to compressor, can not adopt grease lubrication.So of United States Patent(USP) No. 5129752 in order to guarantee reliability, known structure provides a passage that is used to guide the sliding parts of oil to constant velocity universal joint.
Yet, in the structure shown in the United States Patent(USP) No. 5129752, have only the oil that surrounds in the crank chamber (control pressure chamber) just to be introduced into passage.Do not have to disclose the conception of guiding oil to the sliding parts of constant velocity universal joint wittingly, therefore can not think and lubricate sliding parts well.For this reason, the reliability of the anti-rotation effect of swing swash plate reduces, and last sliding parts is killed, and final compressor is lockable.
The purpose of this invention is to provide a kind of oblique tray type compressor and swashplate type compressor, it remains under the good lubricating status sliding parts of swash plate and piston shoes or rotation-preventing mechanism, to improve reliability.
Summary of the invention
According to first aspect of the present invention; A kind of oblique tray type compressor is provided; Said oblique tray type compressor is provided with at least one transmission shaft 104, swash plate 108, piston 112, cylinder block 111, paired piston shoes 109 or the like; High pressure oil storage chamber 122 and Oil Guide road 124 that it also has the device 121 that is used for from the refrigerant gas separating oil, is used to store the oil of separating, said Oil Guide road 124 have the end that is communicated with high pressure oil storage cell 122 and towards the other end of the sliding parts opening of piston shoes 109.This feasible oil can be supplied with the sliding parts between swash plate 108 and the piston shoes 109, can make sliding parts be in good lubricating status, and can make compressor improve reliability.
Preferably, Oil Guide road 124 is arranged on transmission shaft 104 or the cylinder block 111, perhaps is arranged on both.This can form Oil Guide road 124 under the situation that does not adopt any particular components.
According to second aspect of the present invention; A kind of swashplate type compressor is provided; Said swashplate type compressor is provided with at least one transmission shaft 4, rotating disk 5, prevents the swing swash plate 6, piston 9 and the central shaft 8 that rotate by rotation-preventing mechanism 7 that this compressor also has the device 35 that is used for from the refrigerant gas separating oil, the high pressure oil storage cell 36 that is used to store the oil of separating and can supply with the Oil Guide road 85 of oil from high pressure oil storage cell 3 to the sliding parts of rotation-preventing mechanism 7.This feasible oil can be supplied with the sliding parts of rotation-preventing mechanism 7, can make sliding parts remain on good lubricating status, and can make compressor improve reliability.
Preferably, compressor is a variable displacement compressor.The present invention is particularly suitable for this variable displacement compressor.
Preferably, Oil Guide road 85 is arranged on the central shaft 8.This has confirmed to be provided with the parts on Oil Guide road.
Preferably, rotation-preventing mechanism 7 is made up of constant velocity universal joint 7, and the sliding parts of this constant speed universal joint 7 is provided with oil and keeps groove 75.This can remain under the good lubricating status sliding parts of constant velocity universal joint 7.
Preferably, the central shaft 8 of support rotation-preventing mechanism 7 is a cantilever support.In this case, for example, be force-fitted in the other end at the center of cylinder block through having a free end and, even cantilever support also can guarantee the sufficient rigidity of central shaft.
As selection, the central shaft 8 that supports rotation-preventing mechanism 7 has an end that is supported by the bearing 44 that is arranged on the transmission shaft 4, and has the other end on the housings such as being supported on cylinder block 11 non-rotatingly.This makes the load that acts on central shaft 8 can remain on two ends, thereby makes compressor can improve reliability, reduces vibration and noise.
Preferably, compressor can guarantee that conversion (converted to) is the 300cc of freon base refrigeration agent HFC134a or above capacity.This is fit to can be used in the big capacity compressor of the air-conditioning system of bus or other large vehicles.
According to the third aspect of the invention; A kind of constant velocity universal joint is provided; Ring 73, outer shroud 71, ball 74 and isolating ring 72 in said constant velocity universal joint comprises, oil keep groove 75 encircle on the approximate mid-section of axial direction, being arranged on 73 and isolating ring 72 between and between isolating ring 72 and the outer shroud 71.Ring 73 became big with the area of contact of isolating ring 72 and isolating ring 72 and outer shroud 71 in this made, can prevent the rising of surface pressure, can eliminate groove in the sliding parts etc., can eliminate the scratch of being worried, and can realize the stable state that slides.
Preferably, between ring 73 and the outer shroud 71, to form spherical sliding parts, the non-sliding parts of spherical sliding parts was provided with oil and keeps groove 75 in isolating ring 72 sliding contacts ground inserted.This can eliminate the formation that suppresses the too much rib shape of sliding mode on the sliding parts, and makes sliding parts keep good lubrication.
Preferably, spherical sliding parts is formed by the periphery of interior ring 73 and the interior week of isolating ring 72 and the interior week of outer shroud 71 and the periphery of isolating ring 72, forms in of these spherical sliding partss week or periphery and is provided with oil and keeps groove 75.This has stipulated the position that oily maintenance groove 75 forms.
Preferably, each oil keeps groove 75 to have by cutting the groove shapes that flat protruding sphere is formed.This makes groove to form at an easy rate, makes oil utilize the interior ring of isolating ring 72 and the sliding parts that outer shroud 73,71 is supplied with isolating ring 72 swimmingly.
Preferably, each oil keeps the rib 75a of groove 75 not form sharp-pointed rib, but forms the shape of circular (R).The scratch that this can eliminate the sliding parts of isolating ring 72 and interior ring and outer shroud 73,71 prevents the coarse of slidingsurface, makes that slip is smooth and easy.
According to fourth aspect of the present invention, a kind of swashplate type compressor is provided, it is provided with the rotation-preventing mechanism of swing disc 6, and said rotation-preventing mechanism is made up of the constant velocity universal joint 7 of the third aspect of the invention.The lack of lubrication that this can eliminate as the sliding parts of the constant velocity universal joint 7 of rotation-preventing mechanism prevents to kill, and improves the reliability of compressor 100.
Preferably, compressor is a variable displacement compressor.This makes compressor 100 can change discharge capacity, is suitable for absorbing from motor the compressor of driving force.
Preferably, compressor has embedded oil separator 35, these oil separator 35 separating oil, and said oil is then directly supplied with the sliding parts of constant velocity universal joint 7.This makes sliding parts as the object of supplying with the oil of separating through oil separator 35, makes rotation-preventing mechanism can obtain good sliding mode.
Preferably, the central shaft 8 that supports constant velocity universal joint 7 has a free end, and has the other end that is used for cantilever support that is fixed in housing 2.Through central shaft 8 being force-fitted in the center of the cylinder block 2 that forms a housing part, even cantilever support also can guarantee central shaft 8 sufficient rigidity.
As selection, the central shaft 8 that supports constant velocity universal joint 7 has an end that is supported by the bearing 44 that is arranged on the transmission shaft 4, and has the other end that is supported by housing 2 non-rotatingly, supports with both-end.This makes it possible to bear the load that acts on central shaft 8 in both sides, and reliability is improved, and vibration and noise are reduced.
Preferably, compressor can guarantee to be converted into the 300cc of freon base refrigeration agent HFC134a or above capacity.This makes big capacity compressor can be used in the air-conditioning system of bus or other large vehicles.
According to the 5th aspect of the present invention, a kind of constant velocity universal joint is provided, wherein, the axial end of interior ring 73 is provided with oil guide slot 73g, 73h, 73i, is used to guide the oil that flows to axial end to flow to the ball groove.Thus, the oil of the axial end of ring can be introduced the ball groove efficiently in flowing to, thereby eliminates the lack of lubrication of sliding parts.
Preferably, oil guide slot 73g, 73h, 73i are the guiding grooves that extends from the inside ball groove that encircles of the axis hole of interior ring.This make end face vertically flow downward and can be introduced into along the oil that the periphery of axle flows or between axle and axis hole, flows in the ball groove of ring, the realization effective lubricating.
Preferably, oil guide slot 73g, 73h, 73i are down the guiding grooves of groove surfaces in the ball groove of ring in extending to.This makes oil in the ball groove, can preferentially introduce the groove surfaces down of tending to lack of lubrication.
Preferably, rotation-preventing mechanism is made up of the constant velocity universal joint of fourth aspect of the present invention, and the outer shroud 71 of constant velocity universal joint 7 is fixed on the swing disc 6, and interior ring 73 is supported by central shaft 8.This sliding parts that a kind of its constant velocity universal joint 7 can be provided is all by lubricated efficiently swashplate type compressor, thereby makes sliding parts lubricated well, and improves the reliability of compressor.
Preferably, compressor also has the Oil Guide road 85 that is used on axial direction from a side of constant velocity universal joint 7 oil being supplied with sliding parts. Oil guide slot 73g, 73h, the 73i of ring are formed on and supply with on the relative side, oily side in being arranged on.In view of the above, even on the end face that tends to the fuel feeding deficiency of the side relative, also can supply with sufficient oil to the sliding parts of constant velocity universal joint with the side that Oil Guide road 85 is set.
Preferably; This compressor also is provided with and is used for from sucking cylinder-bore and by the oil separator 35 of the fluid separating oil component of cylinder-bore compression and the high pressure oil storage cell 36 that is used to store this oil of separating, will supplying with to constant velocity universal joint 7 through Oil Guide road 85 from the oil of high pressure oil storage cell 36.This makes lubricant oil from compressed fluid, to separate, thereby can prevent that oil from mixing mutually with compressed fluid, effectively utilizes lubricant oil.
Preferably, compressor is a variable displacement compressor.This makes compressor 100 can change discharge capacity, is suitable for absorbing from motor the compressor of driving force.
Preferably, the central shaft 8 that supports constant velocity universal joint 7 has a free end, and has and be fixed in the other end that housing 2 is used for cantilever support.Through central shaft 8 being force-fitted in the center of the cylinder block 2 that forms a housing part, even cantilever support also can guarantee central shaft 8 sufficient rigidity.
As selection, the central shaft 8 that supports constant velocity universal joint 7 has an end that is supported by the bearing 44 that is arranged on the transmission shaft 4, and has the other end that is supported by housing 2 non-rotatingly, supports with both-end.This makes it possible to bear the load that acts on central shaft 8 in both sides, and reliability is improved, and vibration and noise are reduced.
Preferably, compressor can guarantee to be converted into the 300cc of freon base refrigeration agent HFC134a or above capacity.This is suitable for can be used in the big capacity compressor of the air-conditioning system of bus or other large vehicles.
Description of drawings
With reference to accompanying drawing, these and other purpose of the present invention, characteristic will become clearer from the description of following preferred embodiment, wherein:
Fig. 1 is the longitudinal sectional view according to the total of the swashplate type compressor of the first embodiment of the present invention, and it showed when being 100% (maximum flow) capacity;
Fig. 2 is first embodiment's the longitudinal sectional view of swashplate type compressor when minimum capacity;
Fig. 3 is the view of explanation oil spurts to the rotation-preventing mechanism of swashplate type compressor;
Fig. 4 is the view of the rotation-preventing mechanism of being made up of constant velocity universal joint shown in axially;
Fig. 5 is the interior ring of constant velocity universal joint and the perspective view of isolating ring;
Fig. 6 is the enlarged view that the oil of constant velocity universal joint keeps groove;
Fig. 7 is the view that the effect of the constant velocity universal joint that is used for swashplate type compressor of the present invention is described;
Fig. 8 is the longitudinal sectional view according to the total of the swashplate type compressor of the second embodiment of the present invention;
Fig. 9 is second embodiment's the longitudinal sectional view of swashplate type compressor when minimum capacity;
Figure 10 is the longitudinal sectional view according to the total of the oblique tray type compressor of the third embodiment of the present invention;
Figure 11 is the longitudinal sectional view according to the total of the oblique tray type compressor of the fourth embodiment of the present invention;
Figure 12 is the longitudinal sectional view according to the total of the oblique tray type compressor of the fifth embodiment of the present invention; With
Figure 13 is the longitudinal sectional view according to the total of the oblique tray type compressor of the sixth embodiment of the present invention.
Embodiment
Following with reference to figure 1-12, swashplate type compressor and the oblique tray type compressor accordinging to constant velocity universal joint of the present invention and adopt this constant speed universal joint are described.
Fig. 1 accordings to the longitudinal sectional view of the employing constant velocity universal joint of the first embodiment of the present invention as the total of swashplate type variable displacement compressor under the running state of maximum pump discharge (100% capacity) of rotation-preventing mechanism, and Fig. 2 has shown the running state of the minimum injection rate (0% capacity) of the compressor of Fig. 1.
In these accompanying drawings, the front case of reference character 1 expression compressor 100, and the rear case of reference character 3 expression compressors 100.The middle casing of being made up of cylinder block 2 is clipped between front case 1 and the rear case 3.These elements link together through the screw that runs through that securing means does not for example show, to form the housing of compressor 100.
The outer shroud 71 of tubulose substantially is installed on the opening 61 of swing disc 6, and said outer shroud 71 forms the part as the structure of the constant velocity universal joint 7 of the rotation-preventing mechanism of illustrated later.Itself and swing disc 6 fuse, and support radial bearing 52 through the small diameter portion 71a of outer shroud 71.And radial bearing 52 is supported by the internal surface of the opening of annular drive dish 5, and waits and fix through compressing (calking).The left end of the small diameter portion 71a of the outer shroud 71 among Fig. 1 is formed with helical thread portion.Nut 54 and the packing ring 55 of screwing with it are connected to radial bearing 52 on the outer shroud 71.
Like this, radial bearing 52 connects drive plate 5 and outer shroud 71 and swing disc 6 with relatively turnable mode, and above-mentioned thrust bearing 53 is clipped between drive plate 5 and the swing disc 6.So through these structures, swing disc 6 and outer shroud 71 can be with drive plate 5 swings, but can stop and not rotating, not receive the influence of the rotation of drive plate 5.
In the present embodiment; Rotation-preventing mechanism as the rotational motion that is used to prevent outer shroud 71 and swing disc 6; What use is known constant velocity universal joint 7 itself, but this rotation-preventing mechanism and its surrounding structure have formed the special characteristic of present embodiment, and this will specify in the back.
The central shaft 8 of support drive dish 5 and swing disc 6 is fixed and is supported on the elongation line of transmission shaft 4 with non rotatable mode by cylinder block 2.For this reason, for example, cylinder block 2 forms porose 22 at its core, and said hole 22 has spline at its axial direction, and the central shaft 8 that inserts in it is formed with corresponding spline projection on its outer surface, and spline and spline projection engage; The shape of cross section in the hole 22 of central shaft 8 and cylinder block 2 can process square or other are polygon-shaped; The hole 22 of central shaft 8 and cylinder block 2 can be linked together by key 23 and keyway; Perhaps, can adopt various other known devices.Like this, in the compressor 100 of present embodiment, constant velocity universal joint 7 forbids that with rotating central shaft 8 is formed for the rotation-preventing mechanism of swing disc 6.
Around swing disc 6, form and above-mentioned cylinder-bore 21 same number of spherical pits 62.The spheric end 91a that forms at first end of same number of connecting rod 91 engages with these pits 62.And the piston 9 that is slidably inserted in the cylinder-bore 21 also is formed with spherical pit 92.The spheric end 91a that forms at the other end of connecting rod 91 engages with these pits 92.
Notice that the spherical pit 62 of swing disc 6 compresses (calk) around the spheric end 91a of connecting rod 91, to prevent separately.Likewise, the spherical pit 92 of piston 9 is pressed on around the spheric end 91b, to prevent separately.Note; In the present embodiment; Swing disc 6 is compacted they are connected to the spheric end 91a and the 91b of connecting rod 91 with piston 9, and still the connection set on these parts of the present invention not only is confined to " compressing (calking) ", also can adopt other connection sets.
The valve plate that reference character 19 expressions are made up of the plate of thick size.On position, be formed with the single at least exhaust port 19a and the suction port 19b that pass valve plate 19 corresponding to cylinder-bore 21.The inlet hole 19b of valve plate 19 is provided with suction valve 95, and said suction valve 95 is processed by the spring steel plate of the thin size of monolithic.The leaf valve that on these parts, forms like suction valve 95, is closed from cylinder-bore 21 sides.And exhaust port 19a is provided with the leaf valve of being processed by the spring steel plate of thin size equally, like the expulsion valve (not shown), and is closed in exhaust chamber 31 sides.When fixing through device shown not and linking together, valve plate 19, suction valve 95 and expulsion valve are sandwiched in and are fixed between cylinder block 2 and the rear case 3.Notice that the break (not shown) of the lifting capacity of restriction expulsion valve is connected on the valve plate 19 through bolt etc.And, when valve plate 19 is clamped by cylinder block 2 and rear case 3 and fixedly the time, also packing ring 20 clamped.Notice that packing ring is used for three positions: between front case 1 and the cylinder block 2, between cylinder block 2 and the valve plate 19 and between valve plate 19 and the rear case 3.
The rear end of rear case 3 has connection control valve 33 on it.This control valve of electronic control system control that does not show; With the big or small arbitrarily hydrodynamic pressure of formation between fluid (refrigeration agent) pressure (being head pressure) in the fluid in suction chamber 32 (refrigeration agent) pressure (being suction pressure) and the discharge chamber 31, and with its pilot pressure chamber (crank chamber) 18 as pilot pressure supply drive plate 5 or swing disc 6.The pilot pressure of introducing pilot pressure chamber 18 is used for controlling the inclination of swing disc 6.Notice that the passage that is used to introduce the passage of control gaseous and be used for gas to the suction side of drainage swing swash plate chamber (crank chamber) is formed on cylinder 2, rear case 3, valve plate 19 etc., but does not show.
The characteristic of present embodiment is described according to Fig. 3 below, that is, is used for oil is supplied to the mechanism of the sliding parts of compressor 100.
In the present embodiment, rear case 3 is provided with in the downstream of discharging chamber 31 and discharges the upright cylindrical cavity 34 that chamber 31 is communicated with.This upright cylindrical cavity 34 has the oil separator 35 that is press fit in it.As shown in Figure 3, chamber 31 gets into the oil of upright cylindrical cavity 34 and the fluid-mixing of refrigerant gas is separated eccentrically from discharging, so that separating oil and refrigerant gas.The gas of separating drains into the refrigerating circuit from oil separator 35 tops, and oil is kept in the high pressure oil storage cell 36 that is provided with across rear case 3 and cylinder block 2.
The oil that is stored in this high pressure oil storage cell 36 utilizes the pressure reduction between the high pressure in high pressure oil storage cell 36 and the crank chamber 18; As shown in Figure 3; Groove (not shown) through on the packing ring 20 that is arranged between rear case 3 and the valve plate 19, being provided with, be arranged on the Oil Guide road 85 on the central shaft 8, be injected on the sliding parts of the rotation-preventing mechanism that constitutes by constant velocity universal joint 7.That is, the approximate centre of central shaft 8 is run through from cylinder block 2 sides in Oil Guide road 85, and near step 82 to crank chamber 18 openings.Like this, spray, realized the sliding mode of the best of constant velocity universal joint 7 through the oil that will separate by oil separator 35 wittingly sliding parts near constant velocity universal joint 7.
Below, with specifying rotation-preventing mechanism and its device on every side.In the present embodiment, employing is the rotation-preventing mechanism of being made up of constant velocity universal joint 7 that uses in automobile or industrial machinery field.Ring 73, isolating ring 72, outer shroud 71 and a plurality of ball 74 in constant velocity universal joint 7 comprises.The outer shroud 71 of constant velocity universal joint 7 is engaged in the opening 61 of swing disc 6 integratedly.And interior ring 73 is connected in central shaft 8 with mode that can axial motion.Central shaft 8 has a free end side and to be fixed in another of cylinder block 2 distolateral, and like this, it not only can not rotate, and can not move axially.So; Be formed on the spline engage grooves on spline projection 81 and the interior ring 73 that is formed on constant velocity universal joint 7 on the free-ended periphery of central shaft 8; So that it can move, and prevent rotation through the swing disc 6 of interior ring 73 on the axial direction of constant velocity universal joint 7.
Like Fig. 4 and shown in Figure 5, be connected in a swing side, be week in outer shroud 71 spherical of constant velocity universal joint 7 of swing disc 6, be formed with a plurality of ball groove 71b that are parallel to central shaft 8.Be supported on another side, be the spherical periphery of the interior ring 73 of central shaft 8, be formed with a plurality of ball groove 73a that are parallel to central shaft 8, said ball groove 73a is corresponding with a plurality of ball groove 71b in spherical interior week.Outer shroud 71 is connected through annular isolation ring 72 with interior ring 73, and isolating ring 72 contacts the interior week of outer shroud 71 and the periphery of interior ring 73 slidably, and a plurality of balls 74 that are in by 72 maintenances of this isolating ring contact under the state of ball groove 71b, 73a.That is to say that constant velocity universal joint 7 has the outer shroud 71 and interior ring 73 that interior week and periphery with isolating ring 72 are combined together slidably, the periphery of said isolating ring 72 and interior ring 73, have minimum gap between the interior week of outer shroud 71.And, as shown in Figure 1, along with the inclination of swing disc 6, ball 74 to-and-fro motion in ball groove 71b, 73a, isolating ring 72 slides between outer shroud 71 and interior ring 73.These parts relative to each other move, so that keep their position relation continuously.
In this case, isolating ring 72 and outer shroud 71 and the interior ring 73 main sliding partss that slide are positioned on the axial two side portions of week and periphery of isolating ring 72.The approximate mid-section of axial direction forms skid-resistant at all non-sliding parts.So in the present embodiment, non-sliding parts is formed with oil and keeps groove 75.That is to say that in structure shown in Figure 6, interior ring 73 is formed with oil and keeps groove 75 on the periphery of the approximate mid-section of axial direction, and isolating ring 72 is formed with oil maintenance groove 75 on the periphery of the approximate mid-section of axial direction.Shown in Fig. 6 amplified, oil kept groove 75 to form through the protruding sphere of ring 73 peripheries in the truncation and the protruding sphere of isolating ring 72 peripheries.In this case, oil keeps two rib 75a of groove 75 to become circle (R), in order to avoid on the part that from the sphere to the plane, changes, form sharp-pointed rib.Note, oil keep groove 75 also can be arranged on isolating ring 72 on the interior week of the approximate mid-section of axial direction with outer shroud 71 on the interior week of the approximate mid-section of axial direction.In this case, week is a concave spherical surface in two, and like this, the oil that forms suitable shape keeps groove 75.
Fig. 7 is illustrated in swing disc 6 and is in to the right the P1 situation that tilts, substantially under the P2 situation and the P3 situation that tilts to the left of erectility, supplies with the state of oil to sliding parts.That is to say; When swing disc 6 is transformed to the P3 situation of inclination to the left from the P1 situation that tilts to the right; The slide outside part A of the outer circumferential side of isolating ring 72 is by the oil lubrication away from the part of outer shroud 71, and the slides within part B in the interior week of isolating ring 72 keeps the oil lubrication in the groove 75 by the oil that remains on of supplying with this sliding parts B.And; When swing disc 6 becomes the P1 situation of inclination to the right from the P3 situation that tilts to the left; The slide outside part A of the outer circumferential side of isolating ring 72 keeps the oil lubrication in the groove 75 by remaining on oil, and the slides within part B of interior all sides of isolating ring 72 is by the oil lubrication away from the interior ring 73 of the part of isolating ring 72.
Like this; In the present embodiment; Through on the approximate mid-section between isolating ring 72, outer shroud 71 and the interior ring 73, keeping groove 75, increased the area of contact of sliding parts for constant velocity universal joint 7 is provided with oil corresponding to the axial direction of the spherical sliding parts of non-sliding parts.And, owing on part, do not have groove corresponding to the sliding parts of spherical sliding parts, so, there is not abrasive danger, can realize stable slip.
As shown in Figure 4, ring 73 is formed with axis hole 73b at its center in this, and said axis hole 73b engages the spline projection 81 of central shaft 8 axially slidably.And except the ball groove 73a with groove surfaces upwards, ring 73 also has two and has towards ball groove 73c, the 73d of the groove surfaces of true dip direction and the ball groove 73e with downward groove surfaces in this.And ring 73 is formed with the oil guide slot 73i that extends to oil guide slot 73g, the 73h of ball groove 73c, 73d and extend to ball groove 73e from axis hole 73b at its front-end face 73f place in this.It is last that this oil guide slot 73g, 73h and 73i are connected in ball groove 73c, 73d, the highest face temperature 73j of 73e, 73k, 73l.Here, " highest face temperature " refers to the orbital groove surface that is positioned at the highest side and the orbital groove on the ring bottom side of bottom side with respect to ball in vertical direction.
In this structure; Directly supply with between orbital groove 73a and the sliding parts between the 71b, interior ring 73 and the isolating ring 72 of oil lubrication ball 74 and interior ring 73 and outer shroud 71 of constant velocity universal joint 7 and the slide part between isolating ring 72 and the outer shroud 71 grades; But; A part of oil of being supplied with flows through the space between ball 74 and orbital groove 73a, the 71b, flows out to the front side.The oil that flows out to the front side is along the front-end face 73f of interior ring 73 and flowing along the periphery of central shaft 8 with the interface place of central shaft 8, and to dirty.In this centre of flowing; Owing to be formed with oil guide slot 73g, 73h, 73i and orbital groove 73c, 73d, the 73e that is connected with the axis hole 73b of interior ring 73; So orbital groove 73c, 73d, the 73e of ring 73 in oil is introduced along oil guide slot 73g, 73h, 73i are with lubricated orbital groove parts.
If these oil guide slot 73g, 73h, 73i are not set; So; The oil that flows to the front side will flow to the interface (periphery of central shaft 8) with central shaft 8 from the front-end face 73f of interior ring 73 downwards; Front-end face 73f from interior ring 73 flows to isolating ring 72 and outer shroud 71 downwards successively again, orbital groove 73c, 73d, the 73e of ring 73 in therefore oil can not flow into.
Through forming such oil guide slot 73g, 73h, 73i, the anti-rotation sliding parts is remained under the good lubricating status, the reliability of anti-rotation effect can be guaranteed, and the reliability of compressor itself can be improved.
And, confirm in abutting connection with minimum capacity parts 82 central shaft 8 remain on spring or other biasing elements 83 that axle go up to be provided with than the large-diameter portion branch, so that swing disc 6 is biased into the maximum capacity side.Control when this biasing element 83 assists to recover this maximum capacity.On the other hand, central shaft 8 remains on spring or other biasing elements 84 that is provided with on the axle at the end face with a side opposed free ends side of being fixed by cylinder block 2 and supporting, to shift the interior ring 73 of constant velocity universal joint 7 onto rear side.This biasing element 84 assists the control compressor capacity to reach minimum side when compressor operating, when compressor stops, making swing disc remain on the small capacity side always, when restarting, can reduce driving force.
Explanation is by the operation of the swashplate type compressor 100 of the present embodiment of above-mentioned configuration below.The application of the best of compressor 100 is the refrigeration compressor as vehicle air conditioner, and therefore in this case, compressor 100 is also explained as the compressor that is used for vehicle air conditioner.
When transmission shaft 4 by internal-combustion engine or be installed in that motor or other external drive source on the vehicle directly drives via belt, driving mechanism or the like and during rotation, the drive plate 5 of disc parts 40 that is connected in transmission shaft 4 through arm 41, pin 42, elongated orifices 51 and arm member 50 is with transmission shaft 4 rotations.Yet when swing disc 6 is connected with drive plate 5 when can rotate in a circumferential direction through radial bearing 52 and thrust bearing 53, its core is supported by nonrotational central shaft 8 via constant velocity universal joint 7, so can not rotate.When drive plate 5 tilted with respect to the imaginary plane perpendicular to transmission shaft 4, it only can swing the amplitude corresponding to this tilt angle size.Thus, a plurality of pistons 9 that are connected with swing disc 6 through connecting rod 91 will to-and-fro motion in cylinder-bore 21.
Thereby expand in the working room that is formed in those chambers on the end face of a plurality of pistons 9 that are in induction stroke, and therefore the pressure step-down, should be pushed the suction valve on the inlet hole 19b that is arranged on valve plate 19 open and flow into by compressed refrigeration agent in suction chamber 32.In contrast, the working room that is formed on the end face of a plurality of pistons 9 dwindles in compression stroke, so the refrigeration agent in it is compressed, pressure raises, and pushes the expulsion valve on the exhaust port 19a that is arranged on valve plate 19 open, is drained into and discharges chamber 31.Transmission shaft 4 revolutions are moving, and once the discharge capacity of compressor 100 is roughly proportional with the length of stroke of piston 9, and this length of stroke is by the tiltangle decision of drive plate 5 and swing disc 6.
Like this; If change the tiltangle of drive plate 5 and swing disc 6; The discharge capacity of compressor 100 will change, so the discharge capacity of the compressor 100 of present embodiment can control through the pressure in the pilot pressure chamber 18 that changes the back pressure that forms all pistons 9 by control valve 33 to the size of the control system indication that does not show.In pilot pressure chamber 18, can introduce the pressure of any size between the low pressure of the high pressure of discharging chambers 31 and suction chamber 32 from control valve 33.Notice that in order to keep the pressure and the leakage that prevents refrigeration agent in the pilot pressure chamber 18, each piston 9 has the side sealing material that is made up of the piston ring 93 that connects above that.
For example; If the pressure in the rising pilot pressure chamber 18, be the back pressure of piston 9; Its balance with the pressure that is formed on the working room on the end face of piston 9 changes, so the position of the public lower dead centre of a plurality of piston 9 is to moving near the position of valve plate 19, up to reaching new balance.Simultaneously, the oscillation center of swing disc 6 is also towards moving near the position of valve plate 19, and therefore, (line that θ is based on perpendicular to central shaft is that θ=0 defines to the tiltangle of swing disc 6 and drive plate 5.Therefore, 100% capacity of Fig. 1 becomes θ maximum, and the minimum capacity of Fig. 2 becomes θ minimum) diminish, the stroke of all pistons 9 diminishes, and compressor 100 can infinitely reduce discharge capacity thus.
Fig. 2 represent that the pressure in the pilot pressure chamber 18 reach maximum in case the lower dead centre of piston 9 basically with near the state of the upper dead center coupling of the position of valve plate 19, the stroke of piston 9 becomes 0 basically, discharge capacity also becomes 0 basically.In this case, the tiltangle of drive plate 5 and swing disc 6 becomes 0 degree basically, so even drive plate 5 rotates with transmission shaft 4, swing disc 6 can not rotated or swing certainly yet, but remains static basically.So all pistons 9 are in upper dead center position basically, can to-and-fro motion in cylinder-bore 21.Yet; In the present embodiment, make the minimum capacity of central shaft 8 confirm that parts 82 lean on (against) on the interior ring 73 of constant velocity universal joint 7, confirm that in abutting connection with minimum capacity parts 82 are provided with biasing element 83; Become 0 degree fully so that prevent tiltangle; Keep some discharge capacities, do not allow it to become zero (0% capacity), thereby improve the responsiveness of next control circle.
In contrast; If the control system of not showing makes control valve 33 actions; So that the pressure in the pilot pressure chamber 18 is reduced to any level up to suction pressure; The back pressure that acts on the piston 9 will diminish; Therefore the compression reaction force that in the working room, is produced by the compression of refrigeration agent will cause the reciprocating lower dead centre of all pistons 9 to move to the direction away from valve plate 19, the position during axial force balance that axial force that causes up to the back pressure (pressure in the pilot pressure chamber 18) of piston 9 and compression reaction force cause.
Therefore, the tiltangle of swing disc 6 and drive plate 5 becomes big, and it is big that the amplitude of oscillating motion becomes, so the stroke of all pistons 9 becomes greatly together, it is big that the discharge capacity of compressor 100 infinitely becomes.Fig. 1 has shown that the pressure in the pilot pressure chamber 18 is minimum, thereby the tiltangle of swing disc 6 and drive plate 5 becomes big, and the discharge capacity of the stroke of piston 9 and compressor 100 becomes the state of maximum flow (100% capacity).
In the compressor 100 of operation like this; Oil is stored in inner with the various sliding partss in the lubricate compressors 100; For example piston 9 and piston hole 21, the outer shroud 71 of the spheric end 91a of connecting rod 91 and the pit 62 of swing disc 6, constant velocity universal joint 7 and isolating ring 72 and interior ring 73 and isolating ring 72 or the like.Oil is along with refrigeration agent transmits and supply with sliding parts together.
As stated, in the present embodiment, the front-end face 73f of interior ring 73 is formed with from axis hole 73b and extends to oil guide slot 73g, the 73h of ball groove 73c, 73d and extend to the oil guide slot 73i of ball groove 73e.It is last that these oil guide slot 73g, 73h and 73i are connected in ball groove 73c, 73d, the highest face temperature 73j of 73e, 73k, 73l.So; The oil that between ball 74 and orbital groove 73a, 71b, flows out and through interior ring 73 and isolating ring 72 and and isolating ring 72 outer shrouds 71 between the space oil that flow to the front side introduce along oil guide slot 73g, 73h, 73i in orbital groove 73c, 73d, the 73e of ring 73, to lubricate orbital groove.
In the present embodiment, oil keep groove to be formed on the non-sliding parts of approximate mid-section of axial direction of the spherical sliding parts that the periphery by interior week of the outer shroud 71 of constant velocity universal joint 7 and isolating ring 72 forms and the spherical sliding parts that forms by the periphery of interior week of isolating ring 72 and interior ring 73 on.That is, in Fig. 5, on the periphery of the protruding sphere of ring 73, oil kept groove 75 on the periphery of the protruding sphere that is formed on isolating ring 72 on the approximate mid-section of axial direction simultaneously in oil maintenance groove 75 was formed on the approximate mid-section of axial direction.So, remain on oil and keep oil in the groove 75 to supply with the sliding parts of the both sides of the spherical sliding parts on the approximate mid-section of axial direction, thus the good sliding mode of ring and outer shroud 73,71 and isolating ring 72 in realizing.
In the present embodiment; Rear case 3 is provided with upright cylindrical cavity 34, and said cylindrical cavity 34 is provided with oil separator 35, and high pressure oil storage cell 36 is provided with across rear case 3 and cylinder block 2; Oil is separated with the fluid-mixing that the refrigerant gas that compressor 100 is discharged is formed eccentrically; With separating oil and refrigerant gas, this oil flows to Oil Guide road 85 from high pressure oil storage cell 36, and utilizes the pressure reduction in high pressure oil storage cell 36 and crank chamber 18; Be directly injected on the sliding parts of constant velocity universal joint 7, thereby make the rotation-preventing mechanism that constitutes by constant velocity universal joint 7 can improve sliding.Through these, the sliding parts of the rotation-preventing mechanism of swashplate type compressor 100 is remained under the good lubricating status, guarantee the reliability of anti-rotating function, and improve the reliability of compressor itself.
Below; Fig. 8 is a longitudinal sectional view; Shown the total of swashplate type compressor 200 under the running state of maximum pump discharge (100% capacity) according to the second embodiment of the present invention; And Fig. 9 is a longitudinal sectional view, has shown the total of swashplate type compressor 200 under the running state of minimum injection rate according to the second embodiment of the present invention.In this second embodiment, transmission shaft 4 is formed with pit 43 at the core towards a side of central shaft 8.This pit 43 has and is arranged in its inner radial bearing (sliding bearing) 44.The end of central shaft 8 is inserted in this radial bearing 44, is used for supporting.That is to say that in first embodiment, 8 of central shafts at one end side are fixing and support by cylinder block (housing) 2, are used for cantilever support; And in a second embodiment, central shaft 8 have by cylinder block 2 support one distolateral, and it is distolateral to have another that supported by transmission shaft 4, forms the both-end supporting structure.Other parts of this structure are similar to first embodiment, therefore omit the explanation to it.
At two end supports central shaft 8, can bear the load that acts on central shaft 8 in both sides through so, compare with cantilever support, rigidity improves, and reliability improves more, and vibration and noise reduce more.Notice that the bearing of centre of support axle 8 differs and is decided to be radial bearing 44, can be on ball bearing (roller bearing).
Figure 10 is a longitudinal sectional view, has shown the total according to the oblique tray type compressor of the third embodiment of the present invention.In above-mentioned first and second embodiments, the present invention is applied to the swashplate type compressor, but in the 3rd embodiment, the present invention is applied to oblique tray type compressor.In oblique tray type compressor 300, front case 110 is connected to the front end of cylinder block 111, and rear case 113 is connected to the rear end of cylinder block 111 through valve plate, valve formation plate and other plate elements 115.The front case 110 that forms crank chamber (pilot pressure chamber) 107 is supported by transmission shaft 104 with cylinder block 111 rotationally.Be transferred to transmission shaft 104 through belt etc. from the driving force that external drive source (for example vehicle motor) is sent to the belt pulley (not shown).
When the core of swash plate 108 moved to lug plate 105 sides, the tilt angle of swash plate 108 increased.The allowable angle of inclination of swash plate 108 is confirmed by the adjacency of lug plate 105 and swash plate 108.When the core of swash plate 108 moved to cylinder block 111 sides, the tilt angle of swash plate 108 reduced.The minimal tilt angle of swash plate 108 is confirmed by swash plate 108 and the adjacency that is arranged on the snap ring 116 on the transmission shaft 104.
The a plurality of cylinder-bore 111a that are formed in the cylinder block 111 hold piston 112.In the back of each piston 112, be provided with a pair of piston shoes 109.These piston shoes 109 are firmly grasped the outer circumference end of swash plate 108 therebetween slidably.Like this, rotatablely moving of swash plate 108 changed the anterior-posterior to-and-fro motion of piston into through piston shoes 109, thereby piston 112 slidably reciprocates in cylinder-bore 111a.
Though show,, discharge chamber 118 and pass through the pressure feed channel connection, and crank chamber 107 is communicated with through drain passage with suction chamber 117 with crank chamber 107.The refrigeration agent that the pressure feed passage will be discharged in the chamber 118 sends crank chamber 107 to.Refrigeration agent in the crank chamber 107 flows out to suction chamber 117 through drain passage.So the oil that is used for the inside in lubricated crank chamber 107 is mixed with refrigeration agent, it circulates in refrigerating circuit with refrigeration agent.Notice that reference character 119 expressions are arranged on the control valve in the pressure feed passage.
Said structure is the known general structure of oblique tray type compressor 300.The feature structure of the oblique tray type compressor 300 of third embodiment of the invention will be described below.In the 3rd embodiment, as first and second embodiments, rear case 113 is provided with the right circular cylinder shape chamber 120 that is communicated with this discharge chamber 118 in the downstream of discharging chamber 118.This right circular cylinder shape chamber 120 has the oil separator 121 that is press fit in it.As mode shown in Figure 1, this oil separator 121 separates from the oil of discharging the upright cylindrical cavity 120 of chamber 118 entering and the fluid-mixing of refrigerant gas eccentrically, thus separating oil and refrigerant gas.The gas of separating drains in the refrigerating circuit from oil separator 121 tops, and oil is kept in the high pressure oil storage cell 122 that is provided with across rear case 113 and cylinder block 111.
Oblique tray type compressor 300 is that with the difference of above-mentioned swashplate type compressor it does not have rotation prevention structure.So; At present embodiment; The oil that is stored in this high pressure oil storage cell 122 is supplied with through the groove (not shown) that is arranged in the packing ring 123, and said packing ring 123 is arranged between rear case 113 and the plate element 115, and oil flows through the Oil Guide road 124 that is arranged on the cylinder block 111; Utilize the pressure reduction between the high pressure in high pressure oil storage cell 122 and crank chamber 107, spray to the sliding parts of swash plate 108 and piston shoes 109.That is to say, Oil Guide road 124 on the periphery of the supporting part of the cylinder block 111 of supporting shaft 104 1 ends rotationally from rear case 113 side shafts to extending to front case 110 sides, and at the sliding parts opening of front case 110 sides towards swash plate 108 and piston shoes 109.Like this, the oil that oil separator 121 is separated is sprayed and is supplied with the sliding parts of swash plate 108 and piston shoes 109 wittingly, realizes the good lubricating status of sliding parts thus, improves the reliability of compressor 100.
Figure 11 is the longitudinal sectional view according to the total of the oblique tray type compressor 400 of the fourth embodiment of the present invention.In the 3rd embodiment, Oil Guide road 124 is formed on the cylinder block 111, and still, in the 4th embodiment, this Oil Guide road 124 is arranged on the transmission shaft 104, rather than is arranged on cylinder block 111.That is to say that Oil Guide road 124 is passed approximate centre from the front end of the transmission shaft 104 of rear case 113 sides and extended axially to front case 110 sides, and at the some upper edge diametric(al) opening that when piston 112 is positioned at upper dead center, just in time is positioned at below the piston shoes 9.So the oil in the high pressure oil storage cell 122 can flow through the groove (not shown) of packing ring 123, the Oil Guide road 124 of transmission shaft 104, wittingly by the sliding parts between injection and supply swash plate 108 and the piston shoes 109.Other parts of this structure are similar to the 3rd embodiment, therefore omit the explanation to it.
Figure 12 is the longitudinal sectional view according to the total of the oblique tray type compressor 500 of the fifth embodiment of the present invention.At present embodiment, the structure of swash plate 108 is processed the structure of two plate elements that stack together via bearing, as the rotating disk and the relation of swinging swash plate of above-mentioned swashplate type compressor.The bearing that is used to roll is inserted between swash plate 108 and the piston shoes 109.That is to say that swash plate 108 is made up of the swash plate main body 108A of the sub-swash plate 108B that has annular, said sub-swash plate 108B supports through radial bearing 126 and thrust bearing 127.In this case, the rotation-preventing mechanism that also has no naturally of swash plate 108.The oil supply structure that is used for separating oil and refrigerant gas and directly oil is supplied with the sliding parts of swash plate 108 and piston shoes 109 is similar to the 3rd embodiment.Oil Guide road 124 is arranged on the cylinder block 111.Other parts of this structure are similar to the 3rd embodiment, therefore omit the explanation to it.
Figure 13 is the longitudinal sectional view according to the total of the oblique tray type compressor 600 of the sixth embodiment of the present invention.At present embodiment, swash plate 108 adopts the 5th embodiment's swash plate 108 to constitute.But Oil Guide road 124 is arranged on cylinder block 111 and transmission shaft 104 on both.In this case; The oil of separating and being stored in the high pressure oil storage cell 122 at oil separator 121 sprays to the sliding parts of swash plate 108 and piston shoes 109 from the Oil Guide road 124a of cylinder block 111 and the Oil Guide road 124b of transmission shaft 104; Therefore the better lubricating status of sliding parts can be expected, the reliability of compressor can be improved.Other parts of this structure are similar to the 3rd embodiment, therefore omit the explanation to it.
In the above-described embodiments, preferably guarantee to be converted into the 300cc of freon base refrigeration agent HFC (hydrofluorocarbon) 134a or above capacity.Thus, can realize to be applied to the big capacity compressor of the air-conditioning system of bus etc.Notice that concerning CO2 refrigeration agent situation for example, the 300cc or the above volume of refrigerant that are converted into HFC134a refer to 100cc or above capacity.
And as above-mentioned, though swashplate type variable displacement compressor and variable swash plate capacity compressors have been described as an example, the present invention is not limited to variable displacement compressor, and it can also be applied to fixed capacity formula compressor.
Though described the present invention with reference to the specific embodiment of selecting for illustrative purposes, obviously, those skilled in the art can be under the situation that does not deviate from basic thought of the present invention and scope make a lot of modifications to this.
Claims (6)
1. compressor comprises:
Transmission shaft (4), it is supported to ground by housing shaft through bearing, and receives the rotary driving force from driving source,
Drive plate (5), it is connected rotation with said transmission shaft, and can tilt with respect to said transmission shaft,
Swing disc (6), it is connected with said drive plate (5) through bearing (52,53), and appears and the identical tilt angle of said drive plate (5), but is prevented to rotate by constant velocity universal joint,
Piston (9), it is connected with said swing disc (6), and to-and-fro motion on the axial direction of said transmission shaft (4), and said piston (9) is inserted in being used to of forming in the said housing and sucks in the cylinder-bore (21) with compressed fluid,
Be used to support the central shaft (8) of said drive plate (5) and said swing disc (6), said central shaft (8) be supported on by said housing (2) on the elongation line of said transmission shaft (4) and
Said constant velocity universal joint, it has:
Be supported on the interior ring (73) of a side,
By the outer shroud (71) that said swing disc (6) supports, it is arranged in said interior ring (73) on every side,
Be placed at and go up form many with interior week of said outer shroud (71) on the periphery of ring (73) in said the ball in the ball groove (74),
Be arranged in said in isolating ring (72) between interior week of periphery and said outer shroud (71) of ring (73), its support said ball (74) and
Oil keeps groove (75), its approximate mid-section at axial direction to be arranged on encircling between (73) and the said isolating ring (72) or between said isolating ring (72) and the said outer shroud (71) in said,
Place to said isolating ring (72) sliding contact said between ring (73) and the said outer shroud (71), forming spherical sliding parts,
Wherein, the outer shroud (71) of constant velocity universal joint (7) is fixed on the said swing disc (6), and interior ring (73) supports by said central shaft (8),
Said spherical sliding parts is formed by the periphery of ring (73) and the interior week of said isolating ring (72) and the interior week of said outer shroud (71) and the periphery of said isolating ring (72) in said; One of periphery that forms said spherical sliding parts is provided with said oil and keeps groove (75), and each oil keeps groove (75) to have by cutting the groove shapes that flat protruding sphere constitutes.
2. compressor as claimed in claim 1 is characterized in that, each oil keeps the rib (75a) of groove (75) not form sharp-pointed rib, but forms circular shape.
3. compressor as claimed in claim 1 is characterized in that, said swashplate type compressor is a capacity-variable type.
4. compressor as claimed in claim 1 is characterized in that,
Said compressor have embedded oil separator (35) and
Said oil separator (35) separating oil, said oil are then directly supplied with the sliding parts of said constant velocity universal joint (7).
5. compressor as claimed in claim 1 is characterized in that, the central shaft (8) that supports said constant velocity universal joint (7) has a free end, and has and be fixed in the other end that is used for cantilever support on the said housing (2).
6. compressor as claimed in claim 1; It is characterized in that; The central shaft (8) that supports said constant velocity universal joint (7) has an end that is supported by the bearing (44) that is arranged on the said transmission shaft (4), and has the other end that is supported non-rotatingly by said housing (2), supports with both-end.
Applications Claiming Priority (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005163054 | 2005-06-02 | ||
| JP2005163054A JP4439434B2 (en) | 2005-06-02 | 2005-06-02 | Constant velocity joint and swing swash plate compressor using the same |
| JP2005-163054 | 2005-06-02 | ||
| JP2005164821A JP2006336590A (en) | 2005-06-03 | 2005-06-03 | Swash plate compressor or swing swash plate compressor |
| JP2005-164821 | 2005-06-03 | ||
| JP2005164821 | 2005-06-03 | ||
| JP2006017314A JP4571914B2 (en) | 2006-01-26 | 2006-01-26 | Swing swash plate compressor |
| JP2006-017314 | 2006-01-26 | ||
| JP2006017314 | 2006-01-26 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101422773A Division CN1912388B (en) | 2005-06-02 | 2006-06-02 | Swash plate compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101230872A CN101230872A (en) | 2008-07-30 |
| CN101230872B true CN101230872B (en) | 2012-08-08 |
Family
ID=37557323
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101422773A Expired - Fee Related CN1912388B (en) | 2005-06-02 | 2006-06-02 | Swash plate compressor |
| CN2008100813919A Expired - Fee Related CN101230872B (en) | 2005-06-02 | 2006-06-02 | Compressor and constant speed joint |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101422773A Expired - Fee Related CN1912388B (en) | 2005-06-02 | 2006-06-02 | Swash plate compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4439434B2 (en) |
| CN (2) | CN1912388B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102691722B (en) * | 2012-04-11 | 2017-11-03 | 上海齐耀动力技术有限公司 | A kind of two degrees of freedom rolling bearing |
| CN102926959B (en) * | 2012-11-07 | 2016-08-03 | 三一重工股份有限公司 | A kind of swash plate plunger pump or motor |
| CN110529333A (en) * | 2018-05-25 | 2019-12-03 | 刘行兵 | Hydraulic motor |
| CN108656785A (en) * | 2018-05-28 | 2018-10-16 | 商丘师范学院 | A kind of Manual pressure fuel feeding picture-drawing device |
| CN112957994A (en) * | 2021-04-01 | 2021-06-15 | 安徽省金天柱农业科技有限公司 | Mixing equipment is used in special fertile production of rich selenium tea-seed oil |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5167492A (en) * | 1991-08-19 | 1992-12-01 | General Motors Corporation | Fluid pumping assembly having a lubrication circuit functioning independent of the orientation of the fluid pumping assembly |
| CN2661958Y (en) * | 2003-11-12 | 2004-12-08 | 上海三电贝洱汽车空调有限公司 | Hemispherical crawler shoe with groove of sloping plate type compressor |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0329586Y2 (en) * | 1985-11-08 | 1991-06-24 | ||
| JP2000080983A (en) * | 1998-07-09 | 2000-03-21 | Toyota Autom Loom Works Ltd | Compressor |
| JP4016556B2 (en) * | 1999-12-17 | 2007-12-05 | 株式会社豊田自動織機 | Compressor |
| JP4042554B2 (en) * | 2001-12-21 | 2008-02-06 | 株式会社豊田自動織機 | Compressor and compressor lubrication method |
| JP4013754B2 (en) * | 2002-12-18 | 2007-11-28 | 株式会社豊田自動織機 | Air conditioner for vehicles |
| JP4211477B2 (en) * | 2003-05-08 | 2009-01-21 | 株式会社豊田自動織機 | Oil separation structure of refrigerant compressor |
-
2005
- 2005-06-02 JP JP2005163054A patent/JP4439434B2/en not_active Expired - Fee Related
-
2006
- 2006-06-02 CN CN2006101422773A patent/CN1912388B/en not_active Expired - Fee Related
- 2006-06-02 CN CN2008100813919A patent/CN101230872B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5167492A (en) * | 1991-08-19 | 1992-12-01 | General Motors Corporation | Fluid pumping assembly having a lubrication circuit functioning independent of the orientation of the fluid pumping assembly |
| CN2661958Y (en) * | 2003-11-12 | 2004-12-08 | 上海三电贝洱汽车空调有限公司 | Hemispherical crawler shoe with groove of sloping plate type compressor |
Non-Patent Citations (1)
| Title |
|---|
| JP特开平9-133149A 1997.05.20 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4439434B2 (en) | 2010-03-24 |
| CN1912388B (en) | 2013-12-11 |
| CN101230872A (en) | 2008-07-30 |
| CN1912388A (en) | 2007-02-14 |
| JP2006336562A (en) | 2006-12-14 |
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