CN107401509A - Oil supply device for compressor and compressor - Google Patents

Abstract

The present invention provides an oil supply apparatus for a compressor, which includes: a pump driven by a rotating shaft of the compressor, the pump including an oil inlet hole and an oil discharge hole, the oil inlet hole being fluidly connected to an oil sump of the compressor, wherein a lubricating oil is stored in the oil sump; an oil supply passage including a first end fluidly connected to the oil drain hole; and a valve member provided in the oil supply passage and configured to perform an opening degree changing operation in response to a pressure difference across the valve member. The invention also provides a compressor comprising the oil supply device.

Description

Fueller and compressor for compressor

Technical field

The present invention relates to a kind of fueller for compressor and one kind to include the fueller Compressor.

Background technology

The content of this part provide only background information related to the present invention, and it may not formed Prior art.

It is well known that need to supply lubricating oil between all parts in compressor, with play radiating, Sealing, reduce the effect such as abrasion.In the prior art, lubricating oil is taken generally by means of refrigerant Band is to part to be lubricated.However, for variable speed compressor such as frequency-changeable compressor, refrigerant The amount of entrained lubricating oil often with the system frequency of compressor (such as drive mechanism or rotary shaft Rotating speed) it is related.In the case where compressor assembly frequency or rotating speed are relatively low, oil supply amount is lubricated May be too low so that the lubricant effect of all parts in compressor declines, and then reduces compressor Performance.In the case where compressor assembly frequency or rotating speed are higher, lubrication oil supply amount again may can It is too high, so as to cause the heat exchange efficiency of the heat exchanger positioned at compressor downstream to decline, but also meeting Cause lubricant in compressor exhausted in short-term, be damaged compressor.

The content of the invention

As described above, need exist for supplying when can solve the problem that (variable speed) compressor slow-speed of revolution operation The effective technology means of shortage of oil.

One purpose of one or more embodiments of the present invention, which is to provide one kind, can improve pressure The fueller of the lubricant effect of contracting machine.

The another object of one or more embodiments of the present invention is to provide a kind of with good profit The compressor of sliding effect.

A further object for one or more embodiments of the present invention be to provide it is a kind of it is simple in construction, into This cheap and highly reliable fueller for compressor.

The another object of one or more embodiments of the present invention, which is to provide one kind, includes above-mentioned confession The compressor of oily device.

According to an aspect of the invention, there is provided a kind of fueller for compressor, including：

Pump, the pump are driven by the rotary shaft of the compressor, and the pump includes fuel feed hole and oil extraction Hole, the fuel feed hole are fluidly connected to the oil sump of the compressor, wherein, the oil sump memory storage There is lubricating oil；

Oil supply gallery, the oil supply gallery include first end, and the first end is fluidly connected to The outage；And

Valve member, the valve member are arranged in the oil supply gallery, and the valve member is configured to Aperture change operation is carried out in response to the pressure differential of the valve member both sides.

Preferably, the valve member is configured to the aperture change when the pressure differential of the valve member both sides becomes big Small and in the valve member both sides pressure differentials become hour aperture and become big.

Preferably, the valve member is configured to when the pressure differential of the valve member both sides is more than or equal to the Closed and during one predetermined value when the pressure differential of the valve member both sides is less than the first predetermined value When open.

Preferably, the valve member includes valve element, valve seat and flexible member, and the flexible member connects The valve element is connected to, to urge the valve towards the direction for making the valve element be separated with the valve seat Core, the valve member are configured so that：Described in being more than or equal to when the pressure differential of the valve member both sides The valve element engages with the valve seat during first predetermined value；And the pressure when the valve member both sides The valve element separates with the valve seat when difference is less than the first predetermined value.

Preferably, the valve seat and/or the valve element include the oil for allowing lubricating oil flow to pass through all the time Road.

Preferably, the valve element includes tapered portion, the tapered portion be constructed to be permeable to engage with valve seat and Separate.

Preferably, the pump includes pump accumulator, and the outage is via the pump accumulator fluid It is communicated to the oil supply gallery.

Preferably, pump oil passage, the pump accumulator and the pump oil are provided with the rotary shaft Passage.

Preferably, pump accumulator is additionally provided between the pump accumulator and the pump oil passage to go out Mouthful, the size of the pump accumulator outlet can be chosen to the lubrication that regulation flows through the pump oil passage Flow-rate ratio between oil and the lubricating oil for flowing through the oil supply gallery.

Preferably, the pump includes pump accumulator, and the outage is via the pump accumulator fluid The oil supply gallery is communicated to, the valve member also includes letting out with what the pump accumulator was in fluid communication Passage is put, the leakage path is configured to release when the pressure differential of the valve member both sides is more than or equal to The pump accumulator is set to be in fluid communication with the oil sump and when the valve member both sides during predetermined value Pressure differential be less than it is described release predetermined value when the pump accumulator is connected with oil sump disconnection, Wherein, the predetermined value of releasing is more than the first predetermined value.

Preferably, the second end opposite with the first end of the oil supply gallery is arranged on institute Near the air entry for stating the compression mechanism of compressor, wherein, the compression mechanism is by the rotary shaft Driving.

Preferably, the second end opposite with the first end of the oil supply gallery is arranged on institute State near the main bearing seat of compressor, wherein, the main bearing seat is configured to support the rotary shaft.

Preferably, the oil supply gallery and the valve member are arranged in the housing of the compressor Side.

Preferably, the oil supply gallery and the valve member are arranged on outside the housing of the compressor Side.

According to another aspect of the present invention, there is provided a kind of compressor, the compressor include above Described fueller.

Preferably, the compressor is variable speed.

Preferably, the compressor is rotary compressor.

It is following at least one according to the advantages of teaching of one or more embodiments of the present invention Person：It can realize and only additionally supply lubricating oil to part to be lubricated when the compressor slow-speed of revolution is run, Solve the problems, such as to lubricate deficient oil supply during compressor slow-speed of revolution operation；Avoid high turn of compressor The problem of lubricating oil supply is excessive during speed operation；And it is not directed to controller, magnetic valve etc. again Miscellaneous, expensive device, simplifies structure, reduces cost and improves reliability.

By provided herein is explanation, other application fields will be apparent.It should be understood that this Particular example and embodiment described in part are for illustration purposes only without being attempt to limitation originally The scope of invention.

Brief description of the drawings

Accompanying drawing as described herein is only in order at illustration purpose and is not intended to limit in any way The scope of the present invention, accompanying drawing are not necessarily drawn to scale, and can zoom in or out some features to show spy Determine the details of part.In the accompanying drawings：

Fig. 1 shows the profile of the compressor according to first embodiment of the invention；

Fig. 2 shows the profile of the compressor according to second embodiment of the invention；

Fig. 3 A show the profile of the compressor according to third embodiment of the invention；

Fig. 3 B show the enlarged drawing of dotted portion in Fig. 3 A；

Fig. 4 A show the profile of the compressor according to four embodiment of the invention；

Fig. 4 B show the enlarged drawing of dotted portion in Fig. 4 A；

Fig. 5 shows showing according to the fueller for compressor of each embodiment of the present invention It is intended to；

Fig. 6 A are shown according to the fueller for compressor of each embodiment of the present invention Profile；

Fig. 6 B show the amplification profile of dotted portion in Fig. 6 A；

Fig. 6 C show the sectional view of the pump along the fuellers intercepted of the dotted line A-A in Fig. 6 B；

Fig. 7 A show the fueller according to the preferred embodiment of the present invention for compressor The profile of valve member, wherein, valve element is in an open position；

Fig. 7 B show the fueller according to the preferred embodiment of the present invention for compressor The profile of valve member, wherein, valve element is in the close position；

Fig. 7 C are shown to be filled according to the fuel feeding for compressor of another preferred embodiment of the present invention The profile for the valve member put, wherein, valve element is away from valve seat；

Fig. 7 D are shown to be filled according to the fuel feeding for compressor of another preferred embodiment of the present invention The profile for the valve member put, wherein, valve element enters close at least a portion of valve seat and valve element In the valve opening of valve seat；

Fig. 7 E are shown to be filled according to the fuel feeding for compressor of another preferred embodiment of the present invention The profile for the valve member put, wherein, valve element engages with valve seat；

Fig. 8 shows changing according to the fueller for compressor of each embodiment of the present invention Type, wherein, show the leakage path being connected with valve member；And

Fig. 9 shows that the relation between the lubricating oil pressure in the rotating speed and pump accumulator of rotary shaft is bent Line, wherein, show that the outlet of pump accumulator is two various sizes of situations.

It should be appreciated that in all these accompanying drawings, corresponding reference numeral instruction is similar or corresponding Part and feature.For purposes of clarity, all parts in accompanying drawing are not marked.

Embodiment

Hereafter description related to the preferred embodiment is substantially only exemplary and is not intended to limit this hair It is bright.

Essential structure below with reference to Fig. 1 descriptions according to the compressor of embodiment of the present invention.To the greatest extent Pipe Fig. 1 shows the compressor in vertical position, it is to be understood that, teachings of the present invention may be used also With suitable for the compressor in obliquity or horizontal level.

As shown in figure 1, compressor 1 is included substantially in the housing 10 of closed circular tubular, housing 10 Top cover 12 and bottom including the main body 11 positioned at middle part He the axial both ends for being fixed to main body 11 13.Suction joint 14 is equipped with the main body 11, for sucking refrigerant, and in top cover 12 On be equipped with exhaust joint 15, for discharge compress after refrigerant.In main body 11 and top cover 12 Between be additionally provided with the dividing plate 16 substantially transversely extended, so as to by compressor housing 10 Portion space is separated into high-pressure side space and low-pressure side space.Specifically, top cover 12 and dividing plate 16 it Between space form high-pressure side space, and space between dividing plate 16 and bottom 13 forms low-pressure side Space.The bottom of housing 10 is also configured with the oil sump 17 for accommodating lubricating oil.

According to the embodiment of the present invention, compression mechanism 20 and warp are equipped with low-pressure side space content The drive mechanism 40 of compression mechanism 20 is driven by rotary shaft 30.Such as in the example depicted in fig. 1, For compressor in the form of screw compressor, compression mechanism 20 includes the determine vortex part being engaged with each other 22 and dynamic vortex part 24.Positioned at the upper end of rotary shaft 30 eccentric crank pin 32 via bushing (not Sign) it is inserted into the hub portion 26 of dynamic vortex part 24, with rotation driving dynamic vortex part 24. The top of rotary shaft 30 is supported by main bearing seat 50, and the bottom of rotary shaft 30 is by countershaft bearing 54 supportings.Main bearing seat 50 and countershaft bearing 54 are fixedly attached to housing by appropriate mode 10.Drive mechanism 40 is, for example, motor, its stator 42 for including being fixed on housing 10 and fixation In the rotor 44 of rotary shaft 30.

Pump oil passage 34 is provided with rotary shaft 30, pump oil passage 34 is included positioned at the same of bottom Heart hole 36 and the eccentric orfice 38 relative to the radial deflection of concentric holes 36, concentric holes 36 are in fluid communication To oil sump 17, and eccentric orfice 38 extensions lead to the eccentric crank pin of rotary shaft 30 from concentric holes 36 32.Pump oil passage 34 is upward by the lubricating oil in oil sump 17 in the presence of power source such as oil pump Guiding, or part to be lubricated is directly fed to, or carried by means of refrigerant to part to be lubricated. The part to be lubricated can include compression mechanism 20, main bearing seat 50 etc..

For compressor, its rotary shaft 30 at least can be in the first rotating speed (herein, Such as it is referred to alternatively as the slow-speed of revolution) and the second rotating speed (herein, such as being referred to alternatively as high rotating speed) Lower operation, wherein, the first rotating speed is less than the second rotating speed.When compressor is run at the low rotational speed, The supply capability of pump oil passage 34 is weaker, compression mechanism 20 can suck by refrigerant carry The amount of lubricating oil is smaller.However, at the low rotational speed, due to the more low original of the pressure of such as back pressure cavity Cause, it is more serious for the leakage situation higher rotation speed of compression chamber in scroll element, thus easily cause Deficient oil supply is lubricated under the slow-speed of revolution.That is, at the low rotational speed, it is necessary to portion to be lubricated to compressor Part carries out extra lubricating oil supply.

On the contrary, when compressor is run at high speed, the supply capability of pump oil passage 34 compared with By force, compression mechanism 20 can suck the lubricating oil more carried by refrigerant so that under high rotating speed Lubricating oil is sufficient.Thus, at high speed, it is not necessary to treat lubricating component and carry out extra lubrication Oil supply only needs to treat a small amount of lubricating oil supply of lubricating component progress, because excessive lubrication The problems such as oil supply may also can cause heat exchanger efficiency to decline.

The problem of for lubricating deficient oil supply under the slow-speed of revolution, provided at the low rotational speed in order to only extra Lubricating oil supply, the invention provides a kind of fueller 100 for compressor (see Fig. 5).

As shown in Figure 1 and Figure 5, fueller 100 includes pump 110, oil supply gallery 120 and valve Component 130 (see Fig. 5), wherein, pump 110 can be arranged on the lower end of rotary shaft 30 and by revolving Rotating shaft 30 drives, and the one end of oil supply gallery 120 is in fluid communication with pump 110 to receive by the pump of pump 110 The lubricating oil sent, its other end are arranged on nearby components to be lubricated, and valve member 130 is arranged on fuel feeding In passage 120 and it is configured to open at the low rotational speed to allow pumped lubricating oil to flow through fuel feeding Passage 120 is to part to be lubricated and closes at high speed to prevent pumped lubricating oil from flowing through Oil supply gallery 120.Thus, the fueller 100 can be realized and incited somebody to action only in the case of the slow-speed of revolution Lubricating oil in oil sump 17 is supplied to part to be lubricated.

As shown in figure 1, oil supply gallery 120 can supply the lubricating oil pumped to compression mechanism Near 20 air entry.

Preferably, as shown in figure 1, oil supply gallery 120 can be arranged on the inner side of housing 10.This The valve member 130 that kind arrangement can protect oil supply gallery 120 and be arranged in oil supply gallery 120 Exempt to be affected by the external environment.

Alternatively, as shown in Fig. 2 at least a portion of oil supply gallery 120 can be arranged on shell The outside of body 10.This arrangement can easily realize fueller on the basis of existing product Improvement is set up, is supplied without tackling because caused by oil supply gallery 120 is arranged on the inner side of housing 10 Interference problem between oily passage 120 and miscellaneous part.In addition, the valve member 130 can also be set Put in oil supply gallery 120 on the part in the outside of housing 10, consequently facilitating to valve member 130 The performance of (or fueller 100) is monitored and maintenance and replacing if necessary.

Preferably, fueller 100 can include multiple oil supply galleries 120, each oil supply gallery Each lubricating oil is supplied to corresponding part to be lubricated.Specifically, Fig. 3 A and 3B are shown The modification of the fueller shown in Fig. 1, wherein, oil supply gallery 120 is separated from each other including two Oil supply gallery：First oil supply gallery includes the first end 122 for being connected to pump 110 and will lubrication Oil is supplied to the second end 124 of the air entry of compression mechanism 20；Second oil supply gallery includes connection Supplied to the first end (not shown) of pump 110 and by lubricating oil to the second of main bearing seat 50 End 126.

Similarly, Fig. 4 A and Fig. 4 B show the modification of the fueller shown in Fig. 2, wherein, Oil supply gallery 120 includes being connected to the first end 122 of pump 110, supplies lubricating oil to compression The second end 124 of the air entry of mechanism 20 and lubricating oil is supplied to the of main bearing seat 50 Three ends 126.In other words, oil supply gallery 120 includes two oil supply galleries：First end 122 Correspond to the first oil supply gallery with the second end 124, and the end 126 of first end 122 and the 3rd Corresponding to the second oil supply gallery.It is appreciated that each oil supply gallery can have shared first end Portion, it is possible to have respective first end.

It is used for below with reference to Fig. 5 to Fig. 9 to be described in detail according to each embodiment of the invention The fueller 100 of compressor.

As shown in figure 5, fueller 100 includes pump 110, oil supply gallery 120 and valve member 130, wherein, the one end of oil supply gallery 120 is connected to pump 110 to allow pump 110 by grease pump Oil supply gallery 120 is delivered to, the other end can be arranged on the nearby components to be lubricated of compressor, valve structure Part 130 is arranged in oil supply gallery 120 to be supplied with allowing and preventing lubricating oil to flow through oil supply gallery 120 To nearby components to be lubricated, the valve member 130 is configured to the pressure differential when the both sides of valve member 130 Closed during more than or equal to first predetermined value to prevent lubricating oil from being supplied to part to be lubricated and work as Opened when the pressure differential of the both sides of valve member 130 is less than first predetermined value to allow lubricating oil to be supplied to Part to be lubricated.

Specifically, when compressor is run at high speed, the supply capability of pump 110 is stronger, makes It is relatively large to obtain the pressure differential of the both sides of valve member 130, and when compressor is run at the low rotational speed, The supply capability of pump 110 is weaker so that the pressure differential of the both sides of valve member 130 is relatively small.Therefore, Above-mentioned first predetermined value is construed as：The both sides of valve member 130 are more than or equal to first predetermined value Pressure differential correspond to the situation run at high speed of compressor, and the both sides of valve member 130 is small In the situation that the pressure differential of first predetermined value is run at the low rotational speed corresponding to compressor.

In the embodiment of the present invention, as shown in Figure 6A, pump 110 can be arranged on rotation The lower end of rotating shaft 30 simultaneously can be by the rotation driving of rotary shaft 30.Reference picture 6B to 6C, pump 110 Including fuel feed hole 114, outage 116 and pump rotor 118, wherein, the pump rotor 118 of pump 110 Operating, with the lubricating oil sucked from fuel feed hole 114 in oil sump 17 and by outage 116 by institute The lubricating oil of suction is expelled to oil supply gallery 120.

Preferably, pump 110 can be completely submerged in oil sump 17 in order to suck in oil sump 17 Lubricating oil, it is also possible by means oil pipe (not shown) is fluidly connected to oil sump 17.

As described above, because valve member 130 is arranged in oil supply gallery 120, thus valve member 130 are divided to oil supply gallery 120 for two parts --- upstream portion and downstream part.Specifically, Between pump 110 or first end 122 and valve member 130, downstream part is located at upstream portion Between valve member 130 and the second end 124.

When the compressor is operating, the rotation driving pump 110 of rotary shaft 30 is so as to by the profit in oil sump 17 Lubricating oil is pumped to the upstream portion of oil supply gallery 120.When the rotating speed of rotary shaft 30 is relatively low, pump 110 pumpability (such as flow of the pressure of the lubricating oil pumped out or the lubricating oil pumped out) It is relatively low, so as to establish relatively low lubricating oil pressure in the upstream portion of oil supply gallery 120, (so that the pressure differential of the both sides of valve member 130 is less than first predetermined value), lubricating oil can be via confession Oily passage 120 is supplied to part to be lubricated.

On the other hand, when the rotating speed of rotary shaft 30 is larger, the pumpability of pump 110 is stronger, makes The lubricating oil pressure obtained in the upstream portion of oil supply gallery 120 is of a relatively high, (so that valve member 130 The pressure differential of both sides is more than or equal to first predetermined value), lubricating oil can not be via oil supply gallery 120 It is supplied to part to be lubricated.

It is pointed out that the downstream part of oil supply gallery 120 is empty with the low-pressure side of compressor all the time Between connect, thus in the case where not considering the pressure loss in oil supply gallery 120, oil supply gallery Lubricating oil pressure in 120 downstream part is substantially invariable, and is substantially equal to low-pressure side space Interior pressure, and the lubricating oil pressure in the upstream portion of oil supply gallery 120 is substantially equal to pump discharge Lubricating oil pressure.Therefore, the pressure differential of the both sides of valve member 130 can be substantially equal to pump discharge pressure Difference between the pressure in the low-pressure side space of power and compressor.And pump discharge head is rotary shaft The function of rotating speed, accordingly, it is believed that valve member 130 enters only in response to the rotating speed of rotary shaft Row opening and closing operation.

In this way, realized according to the above-mentioned configuration of the present invention：When the rotating speed of rotary shaft 30 is relatively low i.e. At the low rotational speed when (so that the pressure differential of the both sides of valve member 130 is less than first predetermined value), it is allowed to To part fuel feeding to be lubricated, and when the rotating speed of rotary shaft 30 is higher i.e. at high speed (so that valve The pressure differential of the both sides of component 130 is more than or equal to first predetermined value) when, prevent to supply to part to be lubricated Oil.This solves the problems, such as compressor part fuel feeding deficiency under the slow-speed of revolution, while prevents in high rotating speed Under fuel feeding it is excessive.

Based on the actual application requirements, it may be determined that the first predetermined value that valve member 130 opens and closes. For example, can based on the actual application requirements, it is determined that rotary shaft is faced when lubrication deficient oil supply occurs Boundary's rotating speed, then the pump discharge head under the critical speed is measured, it is predetermined so as to calculate first Value.Then, corresponding valve member is being selected according to first predetermined value.However, it is possible under occurring State rough sledding：According to the first predetermined value having calculated that, can not or it is difficult to find matching Valve member, this just needs, it is determined that after critical speed, suitably to adjust the size of pump discharge head, To adapt to existing valve member.

The regulation of first predetermined value (or pump discharge head) will be hereinafter described in detail.

In a preferred embodiment of the invention, as shown in Figure 6B, pump 110 also includes pump oil storage Room 112, pump accumulator 112 are arranged between the outage 116 of pump 110 and oil supply gallery 120, Such as it is arranged on the lower section of outage 116 so that the lubricating oil pumped is into oil supply gallery It can be accumulated before 120 in pump accumulator 112.Lubricating oil pressure in pump accumulator 112 can To be considered as pump discharge head, it is thus possible to so that pump discharge head is more steady.In rotary shaft In the case that 30 rotating speed is constant (such as equal to critical speed), pump accumulator 112 can be adjusted Interior pressure, to be adapted to the specification of existing valve member.

For example, can pressure sensor be set in pump accumulator 112 to monitor pump accumulator 112 Interior lubricating oil pressure.First, determined that the critical of lubrication shortage of oil occurs according to real work demand Rotating speed, pump storage is then calculated according to the specification (corresponding to first predetermined value) of existing valve member The pressure that the planted agent of grease chamber 112 reaches, then when the rotating speed of rotary shaft 30 is equal to critical speed, (example Such as by the way that the lubricating oil in pump accumulator 112 is released operation) by the profit in pump accumulator 112 Lubricating oil pressure (i.e. pump discharge head) is adjusted to the above-mentioned pressure that should reach.

It is pointed out that the rule of suitable valve member according to practical operation demand, can also be selected Specification of lattice, the specification of oil supply gallery and pump etc..

Preferably, pump 110 can also be configured to pump lubricating oil to the pump oil passage 34 of compressor. Specifically, as shown in Figure 6B, the pump accumulator 112 of pump 110 is fluidly connected to pump oil passage 34 Concentric holes 36.

This arrangement makes pump oil passage 34 and oil supply gallery 120 share a pump 110 so that compression The structure of machine is simpler compact.

It is highly preferred that the lower end of rotary shaft 30 can be provided with eccentric driving part 35, the bias is driven One end (upper end as shown in Figure 6B) of moving part 35 be fixedly attached to rotary shaft 30 and with one of Rotate, the other end (lower end as shown in Figure 6B) is mounted slidably in an eccentric manner body In the pump rotor 118 of pump 110 (as shown in Figure 6 C), to drive pump rotor 118.The bias The connecting hole 39 in through-hole form can be provided with actuator 35, by pump accumulator 112 with Concentric holes 36 are in fluid communication.

It is highly preferred that as shown in figs. 6b and 6c, pump accumulator 112 also includes pump accumulator and exported 113, the pump accumulator exports 113 between pump accumulator 112 and connecting hole 39, so as to Enough play throttling action.Specifically, the aperture of pump accumulator outlet 113 or size are optional , or the pump accumulator outlet 113 be easy for change, be suitable for regulation and flow through pump oil passage Flow-rate ratio between 34 lubricating oil and the lubricating oil for flowing through oil supply gallery 120.Pump accumulator exports 113 aperture or the selection of size or replacing can adjust pump discharge head, can also adjust pump storage The responding ability of pump discharge head in grease chamber 112 to the rotation speed change of rotary shaft 30.

Specifically, less first aperture (being, for example, 2mm) of pump accumulator outlet 113 can drop Lubricating oil in low pump accumulator 112 flows into the amount of concentric holes 36 so that in pump accumulator 112 Lubricating oil pressure with rotary shaft 30 rotating speed increase and relatively quickly increase.

By comparison, larger the second aperture (being, for example, 5mm) meeting of pump accumulator outlet 113 Increase the amount that the lubricating oil in pump accumulator 112 flows into concentric holes 36 so that pump accumulator 112 Interior lubricating oil pressure is as the rotating speed of rotary shaft 30 increases and will be relatively slowly increases.

Especially, Fig. 9 shows that the aperture size of pump accumulator outlet 113 turns to rotary shaft 30 The influence of the relation between lubricating oil pressure in speed and pump accumulator 112.As shown in figure 9, work as When the aperture of pump accumulator outlet 113 is 2mm (less first aperture), pump accumulator 112 Interior lubricating oil pressure is higher, and the lubricating oil pressure with the rotating speed of rotary shaft 30 increase and promptly Increase.Ground can be contrasted, when the aperture of pump accumulator outlet 113 is 5mm (larger the Two apertures) when, the lubricating oil pressure in pump accumulator 112 is relatively low, and the lubricating oil pressure is with rotation The rotating speed of rotating shaft 30 increases and slowly increased.Thus, it is possible to by adjusting pump accumulator outlet 113 Aperture adapt to the application of valve member 130 and sensitivity.

On the other hand, the aperture of pump accumulator outlet 113 diminishes and can hindered in pump accumulator 112 Lubricating oil enters concentric holes 36, is supplied so as to reduce by pump oil passage 34 to part to be lubricated Lubricants capacity or ratio, supplied on the contrary, increasing by oil supply gallery 120 to portion to be lubricated The lubricants capacity or ratio of part.Thus, the aperture for exporting 113 by selecting or changing pump accumulator Or size, the quantity delivered or ratio of each lubricating oil feed path can be reasonably distributed, realizes profit The optimal supply of lubricating oil.

Fig. 7 A to Fig. 7 B show the fueller for compressor according to embodiment of the present invention The example of 100 valve member 130.Valve member 130 can include substantially cylindrical valve chest 131st, it is fixed on the end plate 136 of first end plate 134 and second at the axial both ends of valve chest 131, holds Put the valve element 132 in valve chest 131 and be arranged between valve element 132 and first end plate 134 Elastic component 138.Valve chest 131, the end plate 136 of first end plate 134 and second define valve The inner space of component 130.The upstream portion with oil supply gallery 120 is provided with first end plate 134 First valve opening 135 of shunting body connection, to allow pumped lubricating oil to flow into valve member 130 Inner space；It is provided with second end plate 136 and is in fluid communication with the downstream part of oil supply gallery 120 The second valve opening 137, with the inner space of the outflow of lubrication oil valve member 130 allowed flow into.

Valve member 130 can be normally open type valve (as shown in figs. 7 a-b), and Fig. 7 A are shown Valve member 130 is in the situation of non-mode of operation, and now, elastic component 138 does not bear any load Lotus --- such as compressive load and tensile load.When fueller 100 operates, lubricating oil is via First valve opening 135 of end plate 134 flows into the inner space of valve member 130.The lubricating oil of inflow Impact valve element 132 is so that valve element 132 be pushed towards the second end plate 136.When rotary shaft 30 Rotating speed it is relatively low i.e. at the low rotational speed when, impact of the lubricating oil to valve element 132 is smaller, and valve element 132 is not Engaged with the second end plate 136, this permission lubricating oil flows through the second valve opening 137 and leaves valve member 130. Constantly increase with the rotating speed of rotary shaft 30, valve element 132 is eventually in the percussion of lubricating oil Lower to be engaged with the second end plate 136, now, the second end plate 136 is used as valve seat, with valve element 132 It is engaged to prevent lubricating oil from flowing through the second valve opening 137, as shown in Figure 7 B.The configuration realizes When the rotating speed of rotary shaft 30 is higher, valve member 130 closes, and then prevents lubricating oil via confession Oily device 100 is supplied to part to be lubricated.It is pointed out that according to the valve member of the application simultaneously It is not limited to be constructed to respond to the pressure differential (rotary shaft of valve member both sides (as described above) Rotating speed) and closed and opening operation, but can be also configured in response to valve member both sides Pressure differential and carry out aperture change operation.

For example, the pressure in the valve member both sides can be also configured to according to the valve member of the application Aperture diminishes when difference becomes big and the pressure differential in valve member both sides becomes hour aperture and becomes big.

Specifically, Fig. 7 C to 7E show the fuel feeding of another preferred embodiment according to the application The valve member of device, the valve member substantially phase that the configuration of the valve member is shown with Fig. 7 A into 7B Together, therefore to identical structure do not repeat.As seen in figure 7 c, the valve element 132 of valve member 130 Including tapered portion 133, the tapered portion 133 be arranged on valve element 132 towards the second end plate 136 (i.e. Valve seat) side, for being engaged with the second end plate 136.Fig. 7 C show valve member 130 Situation in non-mode of operation, now, elastic component 138 do not bear any load --- as pressed Contracting load and tensile load.When fueller 100 operates, lubricating oil is via first end plate 134 The first valve opening 135 flow into valve member 130 inner space.The lubricating oil impact valve element 132 of inflow So as to which valve element 132 be pushed towards the second end plate 136.Exist when the rotating speed of rotary shaft 30 is relatively low When under the slow-speed of revolution, lubricating oil is weaker to the percussion of valve element 132, and valve element 132 is only oriented towards second End plate 136 is moved but not engaged with the second end plate 136, and this allows lubricating oil to flow through the second valve opening 137 Leave valve member 130.Increase with the rotating speed of rotary shaft 30, the percussion increase of lubricating oil, So that valve element 132 moves further towards the second end plate 136, when valve element 132 is close to the second end plate 136 but when not yet being engaged with the second end plate 136 (as illustrated in fig. 7d), the tapered portion of valve element 132 133 at least a portion can be entered in the second valve opening 137 so that the permission of the second valve opening 137 The effective cross-sectional area that lubricating oil flow passes through reduces, i.e. and the aperture of valve member 130 reduces, from And the flow for flowing through the lubricating oil of valve member 130 is reduced.With turning for rotary shaft 30 Fast constantly increase, valve element 132 (tapered portion 133) eventually under the percussion of lubricating oil with Second end plate 136 (valve seat) engages, and so as to prevent lubricating oil from flowing through the second valve opening 137, such as schemes Shown in 7E.This configuration realizes：In the rotating speed increase of rotary shaft 30, valve member 130 is opened Degree diminishes, and then preferably reduces and supplied via fueller 100 to the lubricating oil of part to be lubricated Flow；Further increase with the rotating speed of rotary shaft 30, valve member 130 closes, and then hinders Only lubricating oil is supplied to part to be lubricated via fueller 100.

Although the valve member according to the application has been described in the preferred embodiment of the application, But it is not limited thereto, but the valve member of all following types, the type can also be included Valve member can be configured to carry out aperture change operation in response to the pressure differential of valve member both sides. Especially, the valve member of the type can be configured to open when the pressure differential of valve member both sides becomes big Degree diminishes and the pressure differential in valve member both sides becomes hour aperture and becomes big.

In other preferred embodiments of the application, the valve member can be also configured to valve The pressure differential of component both sides becomes larger and so that its aperture tapers into, especially so that flows through The flow of the lubricating oil of the valve member is gradually reduced.

In a preferred embodiment, oil duct can be opened up on the second end plate 136 and/or valve element 132 (not shown) so that still allow lubricating oil (such as a small amount of lubricating oil) when end plate engages with valve element Valve member 130 is flowed through to be supplied.This can also ensure height when such as other fuel supply paths fail Lubricating oil supply under rotating speed.

In a preferred embodiment, as shown in figure 8, fueller 100 can also be logical including releasing Road 140.Leakage path 140 can be in fluid communication with pump accumulator 112, with pump accumulator 112 Lubricating oil is released to oil sump 17 when interior lubricating oil pressure is too high.

Specifically, normally close valve (not shown) can be provided with leakage path 140.The normally close valve It can just be opened when valve member 130 closes.Especially, the normally close valve is configured in valve member The pressure differential of 130 both sides, which is more than or equal to when releasing predetermined value, just to be opened, wherein, the predetermined value of releasing More than above-mentioned first predetermined value, so as to prevent after being closed because of valve member 130 valve member 130 and/or Lubricating oil pressure moment in pump accumulator 112 rise and to valve member 130, oil supply gallery 120 And/or pump 110 causes to damage.

As shown in figure 8, the first end 142 of leakage path 140 can be connected to valve member 130 Such as the valve chest 131 of valve member 130 is connected to, its second end 144 can be with oil sump 17 It is in fluid communication.

In other alternative preferred embodiments, the first end 142 of leakage path 140 can be with It is connected to the upstream portion of pump accumulator 112 or oil supply gallery 120.

It is pointed out that including but not limited to it is vortexed according to the compressor of embodiment of the present invention Compressor；Pump according to the fueller for compressor of embodiment of the present invention can be volume Formula pump, such as impeller pump.

Can be preferably purely mechanic according to the valve member of the fueller for compressor of the present invention Formula valve member, i.e., can be independent of the device of the complex and expensives such as control device, calutron But only the rotating speed (or pressure differential of valve member both sides) of rotary shaft is responded and opened With the valve member of closed procedure, this simplifies structure, reduces cost, and improve reliability.

However, it is not limited to according to the valve member of the fueller for compressor of the present invention pure Mechanical valve component.Alternatively, valve member of the invention also may incorporate such as control device, The servicing units such as electronic device, calutron, sensing element open and close operation to perform.

More importantly, overcome according to the fueller for compressor of the present invention and supplied under the slow-speed of revolution The defects of shortage of oil.

Although in preferred embodiment described herein, the valve structure for the fueller of compressor Part be described as being configured to when the pressure differential of valve member both sides is more than or equal to first predetermined value close with And opened when the pressure differential of valve member both sides is less than first predetermined value, but teachings of the present invention not office It is limited to this.Especially, can be with according to the valve member of the fueller for compressor of the present invention Be constructed to respond to valve member both sides pressure differential or differential pressure range and carry out aperture change operation.This A little remodeling and modification can be obtained based on the actual application requirements by those skilled in the art, and be each fallen within In the range of teachings of the present invention.

It is appreciated that variable speed compressor, the variable speed pressure can be included according to the compressor of the application The rotating speed of the rotary shaft of contracting machine is variable and including at least two working speed.For example, the variable speed Compressor includes frequency-changeable compressor.

It is further appreciated that such as screw compressor etc can not only be included according to the compressor of the application Rotary compressor, reciprocating compressor can also be included.

It is pointed out that in text the directional terminology such as front, back, left, right, up, down ginseng Examine the purpose merely for description, not to embodiments of the present invention direction in actual applications and Orientation is construed as limiting.

Although the various embodiments of the present invention are described in detail herein, it should be appreciated that, this hair The bright embodiment for being not limited to be described in detail and show here, in the reality without departing from the present invention Other modifications and remodeling are may be effected by one skilled in the art in the case of matter spirit and scope.Institute There are these modifications and remodeling to be within the scope of the present invention.

Reference numerals list

1 compressor

10 housings

11 main bodys

12 top covers

13 bottoms

14 suction joints

15 exhaust joints

16 dividing plates

17 oil sumps

20 compression mechanisms

22 determine vortex parts

24 dynamic vortex parts

26 hub portions

30 rotary shafts

32 eccentric crank pins

34 pump oil passages

35 eccentric driving parts

36 concentric holes

38 eccentric orfices

39 connecting holes

40 drive mechanisms

42 stators

44 rotors

50 main bearing seats

54 countershaft bearings

100 fuellers

110 pumps

112 pump accumulators

113 pump accumulators export

114 fuel feed holes

116 outages

118 pump rotors

120 oil supply galleries

122 first ends

124 the second ends

126 the second ends, the 3rd end

130 valve members

131 valve chests

132 valve elements

133 tapered portion

134 first end plates

135 first valve openings

136 second end plates

137 second valve openings

138 elastic components

140 leakage paths

142 first ends

144 the second ends.

Claims (17)

1. a kind of fueller for compressor, including：

Pump, the pump are driven by the rotary shaft of the compressor, and the pump includes fuel feed hole and oil extraction Hole, the fuel feed hole are fluidly connected to the oil sump of the compressor, wherein, the oil sump memory storage There is lubricating oil；

Oil supply gallery, the oil supply gallery include first end, and the first end is fluidly connected to The outage；And

Valve member, the valve member are arranged in the oil supply gallery, and the valve member is configured to Aperture change operation is carried out in response to the pressure differential of the valve member both sides.

2. the fueller according to claim 1 for compressor, wherein, the valve member The aperture when the pressure differential of the valve member both sides becomes big is configured to diminish and in the valve member two The pressure differential of side becomes hour aperture and becomes big.

3. the fueller according to claim 1 for compressor, wherein, the valve member It is configured to that institute is closed and worked as when the pressure differential of the valve member both sides is more than or equal to first predetermined value State when the pressure differentials of valve member both sides is less than the first predetermined value and open.

4. the fueller according to claim 3 for compressor, wherein, the valve member Including valve element, valve seat and flexible member, the flexible member is connected to the valve element, makes institute with direction State valve element and direction that the valve seat separates urges the valve element, the valve member is configured so that：When The valve element and the valve when pressure differential of the valve member both sides is more than or equal to the first predetermined value Seated connection closes；And the valve element when the pressure differential of the valve member both sides is less than the first predetermined value Separated with the valve seat.

5. the fueller according to claim 4 for compressor, wherein, the valve seat and / or the valve element include allowing the oil duct that passes through of lubricating oil flow all the time.

6. the fueller according to claim 4 for compressor, wherein, the valve element bag Tapered portion is included, the tapered portion is constructed to be permeable to engage and separate with valve seat.

7. the fueller according to claim 1 for compressor, wherein, the pump includes Pump accumulator, the outage are fluidly connected to the oil supply gallery via the pump accumulator.

8. the fueller according to claim 7 for compressor, wherein, the rotary shaft In be provided with pump oil passage, the pump accumulator and the pump oil passage.

9. the fueller according to claim 8 for compressor, wherein, stored up in the pump The outlet of pump accumulator, the chi of the pump accumulator outlet are additionally provided between grease chamber and the pump oil passage It is very little to be chosen to regulation and flow through the lubricating oil of the pump oil passage and flow through the profit of the oil supply gallery Flow-rate ratio between lubricating oil.

10. the fueller according to claim 3 for compressor, wherein, the pump bag Pump accumulator is included, the outage is fluidly connected to the oil supply gallery, institute via the pump accumulator State the leakage path that valve member also includes being in fluid communication with the pump accumulator, the leakage path construction Into when the valve member both sides pressure differential be more than or equal to release predetermined value when make the pump accumulator with The oil sump is in fluid communication and when the pressure differential of the valve member both sides is less than the predetermined value of releasing When the pump accumulator and the oil sump is disconnected connect, wherein, described in the predetermined value of releasing is more than First predetermined value.

11. the fueller for compressor according to any one of claim 1 to 10, Wherein, the second end opposite with the first end of the oil supply gallery is arranged on the compressor Compression mechanism air entry near, wherein, the compression mechanism is driven by the rotary shaft.

12. the fueller for compressor according to any one of claim 1 to 10, Wherein, the second end opposite with the first end of the oil supply gallery is arranged on the compressor Main bearing seat near, wherein, the main bearing seat is configured to support the rotary shaft.

13. the fueller for compressor according to any one of claim 1 to 10, Wherein, the oil supply gallery and the valve member are arranged on the case inside of the compressor.

14. the fueller for compressor according to any one of claim 1 to 10, Wherein, the oil supply gallery and the valve member are arranged on the hull outside of the compressor.

15. a kind of compressor, the compressor is included according to any one of claim 1 to 14 institute The fueller for compressor stated.

16. compressor according to claim 15, wherein, the compressor is variable speed.

17. compressor according to claim 16, wherein, the compressor is rotary compression Machine.